Rotary device for a tree-handling device

Abstract

An object of the invention is a rotary device (10) for a tree-handling device (300). The rotary device includes a shaft 116) configured to be suspended from a boom arm (204); a frame (11) supported coaxially on the shaft by means of bearings (25, 35), wherein the bearings include a first bearing (25) configured to bear radial forces transmitted from the frame to the shaft and a second bearing (35) configured to bear the frame axially on the shaft; a drive arrangement (55) for rotating the frame relative to the shaft, wherein the drive arrangement includes a first, driven set of teeth (53' ) and a second, driving set of teeth (33' ) for rotating the frame relative to the shaft. The bearing that is configured to bear the frame axially is a loaded tapered roller bearing (36) without a preloading that is configured to act as the sole bearing that bears the frame axially; the tapered roller bearing includes an inner ring (18) and an outer ring (19), wherein the inner ring is configured to be borne by the shaft and the outer ring is configured to bear the frame; an axial play (14) is arranged between the frame and the shaft, which axial play is configured to allow the frame to perform an axial movement determined by the play in a situation of an impact acting on the rotary device, and the sets of teeth of the drive arrangement and the first bearing are configured to allow said play (14).

Description

[0001] ROTARY DEVICE FOR A TREE-HANDLING DEVICE

[0002] The object of the invention is a rotary device for a treehandling device, wherein the rotary device includes

[0003] - a shaft configured to be suspended from a boom arm,

[0004] - a frame supported coaxially on the shaft by means of bearings, wherein the bearings include a first bearing configured to bear radial forces transmitted from the frame to the shaft and a second bearing configured to bear the frame axially on the shaft,

[0005] - a drive arrangement for rotating the frame relative to the shaft, wherein the drive arrangement includes a first, driven set of teeth arranged in connection with the shaft and a second, driving set of teeth arranged in connection with a drive motor for driving said first set of teeth and rotating the frame relative to the shaft,

[0006] - pressure-medium distribution means between the shaft and the frame as well as first fittings on the side of the shaft and second fittings on the side of the frame that are connected to said distribution means.

[0007] The rotary device or rotator is provided between the boom arm of the tree-harvesting machine and the actual tree-handling device. More specifically, the rotary device is located in this case at the top of a felling mechanism, i.e. , a tilt. The felling mechanism can also be called an inclination mechanism. The felling mechanism can be an arm attached to the rotator. It is connected in an articulated manner at the bottom to the frame of the tree-handling device. The felling mechanism is operated by a hydraulic cylinder. The felling mechanism is used to pivot the tree-handling device into an upright position for the felling of a tree and to move it into a horizontal position for the delimbing and cutting to length of the tree. The felling mechanism allows the tree-handling device to hang freely.

[0008] Rotary devices with an unlimited rotation are known. In this case, one can also speak of a fully rotatable rotary device. It is also known to run hydraulics and electrics straight through the rotary device, which helps to enable a full rotatability .

[0009] The international patent application with the publication number WO 2019 / 193255 discloses a rotary device. In this document, the fully rotatable frame of the rotary device is mounted in a bearing arrangement on a central shaft . The bearing arrangement consists in a ball bearing arranged in the upper part of the rotary device and a thrust bearing arranged in the lower part of the rotary device. The ball bearing receives the radial loads that occur between the frame and the shaft. The thrust bearing, in turn, bears the weight of the tree-handling device attached to the frame of the rotary device. The thrust bearing is thus subjected to a downward axial load. However, with this type of bearing arrangement, the ability of the structure to withstand impact forces is poor, which reduces the durability of the rotary device. An ability to withstand impact forces is necessary, for example, whenever the tree-handling device hits the ground with force during its operation. Such impacts have an adverse effect on the durability of a rotary device .

[0010] The object of this invention is to provide a rotary device for a tree-handling device that is improved in terms of its durability and in particular its ability to withstand impacts compared to the prior art. The characteristic features of a rotary device according to the invention are set out in patent Claim 1. A rotary device according to the invention includes a tapered roller bearing.

[0011] The tapered roller bearing is configured to bear the frame axially on the shaft.

[0012] The tapered roller bearing is loaded by the force of gravity in the rotary device. The load on the tapered roller bearing is thus produced in a work situation by the tree-handling device suspended from the rotary device, and more specifically from its frame. In a work situation, the tree-handling device is suspended in the air, its weight borne by the rotary device.

[0013] The tapered roller bearing can also be provided in the rotary device without a preloading. This is in part rendered possible by its loading by the force of gravity.

[0014] The tapered roller bearing is also the sole bearing in the rotary device that bears the frame axially. In other words, there is no counterpart to this bearing in the rotary device.

[0015] When the tapered roller bearing replaces, for example, the thrust bearing known from the prior art in the lower part of the rotary device, the tapered roller bearing can withstand axial loads in both directions. As a result, the overall structure of the rotary device is also rendered more resistant to axial impacts from below. In particular, the tapered roller bearing makes it possible to provide an axial play for the frame of the rotary device. This makes it possible to implement an axial movement of the frame of the rotary device that protects structures of the rotary device from impact forces, for example when the tree-handling device hits the ground with force. The integrated axial play provided in the upper part of the rotary device, which can be configured there in connection with a radial bearing, improves the ability of the rotary device to withstand the impacts to which it is subjected. In other words, impacts acting on the rotary device from below thus no longer act on the bearings or on the structures of the rotary device in general to the same degree in terms of a stress placed on the same, but the forces they produce are transferred in a controlled manner via the frame to the shaft. This occurs through designated contact surfaces of the frame and the shaft.

[0016] The remaining contiguous surfaces between the frame and the shaft of the rotary device are configured to allow the axial movement provided for the frame. These parts include, for example, the bearing that receives radial forces, for example in the upper part of the rotary device. These parts further include a toothed transmission that can produce a rotational movement in the rotary device.

[0017] In addition to providing an improved absorption of axial loads, the tapered roller bearing also provides an ability to withstand radial loads in the lower part of the rotary device. The bearing angle of the tapered roller bearing, which is configured to be slight, also helps in this connection. Other, additional advantages and features of the invention will become apparent from the detailed description and the attached claims.

[0018] The invention, which is not limited to the embodiment presented in the following, will be described in more detail with reference to the accompanying drawings, wherein Figure 1 shows schematically an example embodiment in which a rotary device according to the invention can be used,

[0019] Figure 2 shows schematically an example of a treehandling device in connection with which a rotary device according to the invention can be used,

[0020] Figures 3 and 4 show an example of a rotary device according to the invention viewed from different directions ,

[0021] Figure 5 shows an example of a rotary device according to the invention as an axial cross section,

[0022] Figures 6a and 6b show the rotary device shown in Figure 5 in a disassembled condition,

[0023] Figure 7 shows the situation, including an enlargement, of the relationship between the parts of the rotary device in connection with the upper bearing in a work situation of the tree-handling device,

[0024] Figure 8 shows the situation, including an enlargement, of the relationship between the parts of the rotary device in connection with the upper and lower bearings in the event of an impact acting on the rotary device from below, and

[0025] Figures 9 and 10 show the rotary device viewed from different directions, wherein the gearwheels belonging to the drive arrangement are visible.

[0026] Figure 1 schematically shows an example of a tree-harvesting machine 200 in an oblique side view. Tree-harvesting machines 200 generally have a crane 202 with a movable working boom assembly 203 arranged on a base machine 201. A tree-handling device 300 is attached, for example in an articulated manner, to the end of the last boom arm of the working boom assembly 203, i.e. to the end of the folding arm 204 here. The base machine 201 is a small excavator here, but it could also be a forestry machine. The crane 202, i.e. , working boom assembly

[0027] 203 here includes a main boom 205 and a folding arm 204. At the end of the folding arm 204 is an adapter 209, from the articulated joint of which the tree-handling device 300 is suspended (by a universal joint part 208) . The articulated connection of the tree-handling device 300 to the folding arm

[0028] 204 as such can be implemented, for example, in any manner known in the prior art and is not limited by the invention. Generally speaking, it can be implemented, for example, by two crosswise oriented pivot joints, more generally by a universal articulated joint 206. This can also be called a link 206' . Put even more generally, the tree-handling device 300 is thus generally suspended from the base machine 201, more specifically here from the working boom assembly 203 of the excavator.

[0029] The rotary device 10, also commonly referred to as a rotary actuator or rotator, is provided between the tree-handling device 300 and the universal articulated joint 206. The treehandling device 300 can be rotated by the rotary device 10. According to one embodiment, this can even occur in a fully rotational manner around the rotation axis R of the rotary device 10 (Figure 4) . In the embodiment shown, the frame 11 of the rotary device 10 can be integrated in the felling mechanism

[0030] 307, for example, i.e. in the arm 308 of the tilt. The rotary device 10 can thus be located, for example, between the arms

[0031] 308. It is equally possible, however, for the rotary device 10 to be implemented as a separate, detachable, i.e. replaceable, component. In this case, the arms 308 or the like can also be connected by a flange connection to a downward facing flange connection surface (Figure 3) configured in the frame 11 of the rotary device 10, more generally to the lower end of the rotary device 10. According to one embodiment, the rotary device 10 can be attached by (4 - 10) bolts 51, for example, to the upper end of the arm 308. The tree-handling device 300 can be attached to the frame 11 of the rotary device 10, for example, by means of a fastening flange 50.

[0032] The felling mechanism 307 can be said to include the arms 308 or a fork (not shown) . These are used to move the tree-handling device 300 into a horizontal position and back into an upright position with the force of a hydraulic cylinder. It is thus also possible to speak of a horizontally positionable treehandling device 300. The upper part of the felling mechanism 307 can be attached to the working boom assembly 203 of the base machine 201 via the rotary device 10, i.e. , rotator by means of a so-called universal joint as mentioned in the foregoing. The rotary device 10 accordingly enables a rotational movement between the tree-handling device 300 and the working boom assembly 203. The shaft orientation in a rotational movement can be approximately vertical, with a possible deviation of, for example, approximately ± 30° from the vertical orientation. The universal joint at the upper part of the rotary device 10 allows the tree-handling device 300 to be placed in a suspended position. A speed of the rotary device 10 can be approximately 30 r / min ± 50%.

[0033] The pressure-medium flow required by the actuators of the treehandling device 300 (e.g. , the saw motor 302) can be supplied from the base machine 201. In this case, it is supplied from a pressure-medium pump of the base machine 201 via the working boom assembly 203 of the crane 202 by means of hoses 303 or, more generally, pressure-medium lines. The pressure-medium pump is operated, for example, by the motor of the base machine 201 to create pressure. Where appropriate, corresponding line systems can also be implemented, for example, for urea or analogous processing fluids, as well as for other liquid substances. This also applies to electrics and / or data communication via cables.

[0034] The base machine 201 of the tree-harvesting machine 200 can be wheeled or, as in this case, be provided with turning caterpillar tracks 207 and a sufficient ground clearance. The wheels and / or caterpillar tracks 207 and the ground clearance make the tree-harvesting machine 200 suitable for off-road use.

[0035] Figure 2 shows a rough depiction of an example of the treehandling device 300 used in the example embodiment of Figure 1. Figure 2 shows the tree-handling device 300 in a side view in a position in which a tree 400 is about to be felled. In the context of the invention, a tree-handling device 300 can be understood in a fairly broad sense. According to some embodiments, it can be, for example, a harvester head, i.e. a multi-purpose harvester head, or it can be just a felling head. A rather typical series of processing operations carried out by a tree-handling device 300 in the case of a harvester head is the cutting down of a tree 400, the delimbing of the tree 400, and the cutting of the delimbed trunk into sections of a specified length as the delimbing progresses. It is equally possible for a processing performed by the tree-handling device 300 to consist in any of the aforementioned operations individually or in various combinations of the same. It can comprise, for example, a delimbing of tree trunks, a cutting to length carried out during delimbing and / or a gathering of one or more delimbed tree trunks for stacking or loading. It is possible for one or a plurality of trees to be processed at a time, wherein in the latter case one can speak of a batch processing of trees. In the case of such a series of operations and a forest machine, the latter is also often called a multipurpose machine. In general, a tree-handling device 300 can be said to include a functional unit 300 ' , the basic parts of which are a cutting device 301 ' , a feeding device 304 and gripping means 305' .

[0036] To turn the functional unit 300, i.e. the tree-handling device 300, the tree-handling device 300 includes an actuator for turning the functional unit 300' between a felling position and a delimbing position. This is often called the tilt. In Figure 2, the tree-handling device 300 is in the felling position. The functional unit 300 ' is thus mainly vertical. The delimbing position is attained by turning the functional unit 300 ' by approximately 90° from the position shown in Figure 2 by means of the actuator. As a result of this rotation, the functional unit 300 ' is mainly horizontal, as shown in Figure 1. The actuator, which belongs to the felling mechanism, for pivoting the functional unit 300 ' can be, for example, a hydraulic cylinder arranged in a housing 306, although it can also be some other actuator that is suited to this purpose.

[0037] The tree-handling device 300 also includes a cutting device 301 ' . The cutting device 301 ' here is a pivotable chain saw 301. It is located at the end of the tree-handling device 300 and thus also at the end of the functional unit 300 ' . The felling, i.e. , cutting down of a tree 400 can be performed with the cutting device 301 ' . In addition, the sectioning of the trunk of the tree 400 to a specified length can also be performed with the cutting device 301 ' . In the case of a chain saw, the cutting device 301 ' includes, in a manner known per serin addition to a cutting chain, a pivotable guide bar, a drive gear for the cutting chain, which rotates the cutting chain around the guide bar, and means for pivoting the guide bar so as to carry out a sawing operation. The guide bar is pressed, i.e. , loaded by said pivoting means against the tree to be sawn. In addition, the pivoting means also returns the guide bar with the cutting chain back to its base position for the next sawing operation .

[0038] When work is performed with the same in a known manner, the tree-handling device 300 generally operates by gripping a tree 400 with the gripping means 305' of the functional unit 300 ' . The gripping means 305' can be, for example, grippers 305 that can be opened and closed. The grippers 305 can also include a cutting function for delimbing the tree 400 of branches. It is also possible for the feeding device 304 to act as gripping means 305' . The feeding device 304 can include, for example, rollers, feeder tracks 304 ' or even a stroke feed. Instead of processing a single tree 400, the gripping means 305' and / or the feeding device 304 can also perform a batch processing of trees. It should be noted that the feeding device 304 is not an essential feature, and it is also possible to implement the tree-handling device 300 without it. In this case, however, the tree-handling device 300 will not include the delimbing feature that is effected when the tree 400 is pulled through the treehandling device 300. It is of course still possible in this case to perform a delimbing operation, for example with a movement of the working boom assembly 203, but it is implemented more efficiently with a feeding device 304.

[0039] After the cutting down of the tree 400 has been carried out with the cutting device 301 ' , the functional unit 300 ' is pivoted into a horizontal position to delimb the tree 400 of branches and cut it into sections of a specified length. The tree-handling device 300 is subsequently moved relative to the tree 400 by the feeder tracks 304' of the feeding device 304. As a result, the tree 400 passes through the functional unit 300 ' . When the grippers 305 are closed, they are positioned tightly against the trunk of the tree 400 and, as the tree 400 moves relative to the functional unit 300 ' , delimbing blades located at the edges of the grippers 305 cut the branches off the tree 400. When a section of a desired length of the tree 400 has been delimbed, the trunk is sawn into a section of a specified length with the cutting chain of the cutting device 301 ' . The delimbing of the tree 400 is subsequently continued by feeding the tree through the grippers 305.

[0040] Figures 3 and 4 show an example of a rotary device 10 according to the invention in a side view from different directions. Figure 5 in turn shows the rotary device 10 according to the invention shown in Figures 3 and 4 as an axial cross section. Figure 6 shows the same rotary device 10 disassembled into two parts. These can be referred to as the shaft side, shown in Figure 6a, and the frame side, shown in Figure 6b. In the embodiment shown, the rotary device 10 is fully rotatable. However, this is not an essential feature of the invention per se . According to one embodiment, the rotary device 10 can be arranged, for example, in the upper part of the felling mechanism 307 in a situation of use. In this case, the outer part of the rotary device 10, which can also be called the rotatable device frame 11, can be integrated into the upper part of the arms 308. A circumferential rotation of this part thus produces a rotation of the tree-handling device 300 in a desired direction, as they are mechanically connected to each other . With reference to Figure 5, the upper part of the device frame 11, more specifically the transverse support 43 of the device frame 11, is supported on the shaft 16. This support is provided by a radial bearing 25 arranged between the device frame 11 and the shaft 16. The bearing 25 holds the shaft 16 and the frame 11 together and in position in relation to each other laterally. The bearing 25 is located immediately underneath the gearwheel 53.

[0041] The lower part of the device frame 11, and more specifically the transverse support 41 of the device frame 11, is supported on the shaft 16. This is achieved by means of a second bearing 35 arranged in connection with the device frame 11.

[0042] The transverse support 43 of the upper part and the transverse support 41 of the lower part of the device frame 11 - i.e. the device frame 11 in general - are securely attached to the arm 308 or to an analogous supporting member of the tree-handling device 300. According to one embodiment, the transverse supports 43 and 41 can be attached, for example, between the arms 308. In the shown embodiment, the attachment of the transverse supports 41, 43 to each other is achieved by means of a frame casing 12 belonging to the frame 11. The frame casing 12 thus joins the transverse supports 41, 43. The tree-handling device 300 can also be connected to the rotary device 10 underneath the rotary device 10.

[0043] In the embodiment of the rotary device 10 shown in Figure 5, the combined bracket and fitting part 23 fastens the shaft 16 and the gearwheel 53 together by means of bolts 39.1. The bolts 39.1 fasten the gearwheel 53 and the shaft 16 together here by means of a flange 15 configured in the upper end of the shaft 16. A small shoulder structure in the flange 15 (reference number 62 in Figure 6a) is sufficient for this purpose. The flange 15 at the end of the shaft 16 and the gearwheel 53 overlap in the centre bore of the gearwheel 53. A shoulder structure is provided in the gearwheel 53 on the inner circumference of the centre bore. The end of the shaft 16, i.e. the widened flange 15 configured at the end of the shaft 16 here, fits into the recess formed in this region of the gearwheel 53.

[0044] Manufacturing a shaft 16 is challenging because of the oil conduits. It demands quality raw materials and a precise machining. As some of the fastening bolts 39.1 are located on the outside of the end 15 of the shaft 16, i.e. in the area of the gearwheel 53, an eccentric load is created during the assembly of the rotary device 10. The part 23 is thus attached to the shaft 16 also with second bolts 39.2. These are used to attach the part 23 to the widened flange 15 configured at the end of the shaft 16.

[0045] In a work situation, the rotary device 10 is also subjected to eccentric loads. In this case, the gearwheel 53 with its bolts 39.1 receives this eccentric load. To take this into account, the second bolts 39.2 are arranged at the end of shaft 16. Small elastic loads are permitted in the structure. The bolts 39.1 and 39.2 are dimensioned according to their breaking strength. When eccentric loads that could break structures are encountered, the bolts 39.2 are easier to replace should they break. By means of the bolts 39.2, it is also possible to make the flange 15 of the shaft 16 narrower. If the flange 15 were wider, the bolts 39.2 would be enough. A smaller shaft 16 and thus also a smaller flange 15 are surprisingly more durable, because the material of the shaft 16 can be of a better quality so that the shaft 16 is more durable. The combined link and fitting part 23 conveys oil acting as the pressure medium, as well as any electrics and / or urea, to the shaft 16. The part 29, i.e. the link bracket, also bears the weight of the tree-handling device 300 via the shaft hole 20 in said bracket. The hole 20 is thus the lower attachment point of the link. Since the link bracket 29 is connected to the shaft 16, the shaft 16 can also be said to be configured to be suspended from the boom arm 204.

[0046] As is known, a tree-handling device 300 needs pressurized oil for its functions. It can additionally need electricity, for example for the operation of valves and / or a data transmission. The pressure of the pressurized oil can be, for example, 250 bar ± 30% while its volumetric flow rate can be approximately 200 1 / min ± 30%. In addition to supply lines, an oil return line is also provided for a corresponding volumetric flow, but its pressure can be only approximately 20 bar ± 30%. Sometimes part of the return oil can be conveyed via a separate line. This part comprises, for example, leakage oil from motors and valves. In other words, two or three lines are needed for hydraulic fluids.

[0047] Figures 3 and 4 show fittings 21 and 22 for the pressure medium as well as leakage lines. They are connected to hoses that run from the base machine 201. The pressure medium enters via the fittings 21, 22, continues through a connection in the lower surface of the fitting part 24 and a channel formed in the shaft 16, and from there continues on through the rotatable distribution means 17 (Figure 5) to the fittings 31, 32 on the outer surface, which are arranged on the side of the frame 11. Hoses 303 that lead to the tree-handling device 300 are connected to these fittings 31, 32. The rotary device 10 can thus be said to include pressure-medium distribution means 17 between the shaft 16 and the frame 11. The rotary device 10 can also be said to include first fittings 21, 22 on the side of the shaft 16 and second fittings 31, 32 on the side of the frame 11, which fittings 21, 22, 31, 32 are connected to the distribution means 17.

[0048] The fitting part 24 is in turn connected by its upper part to the link bracket 29, for example by means of a pin. The fitting part 24 and the link bracket 29 can also be one and the same piece. Of course, it is also possible here to use other types of articulated joints that transmit torque but still allow a rocking motion in the horizontal plane.

[0049] The fitting 22 leading from the fitting part 24 via a channel in the shaft 16 to the fitting 32 functions in the same way as the flow of oil from the fitting 21 via its channel to the fitting 31. The pressure-medium channels, which are not shown here, can initially run inside the shaft 16 from its upper end axially towards the lower end of the shaft 16 in a position of operation of the rotary device 10. At a distance from the upper end of the shaft 16, the channel changes direction so as to become at least one and preferably more than one radial channels in the shaft 16. In other words, the channels thus run transversely to an outlet in the outer surface of the shaft 16. Thus, for each axial pressure-medium channel, there can be a plurality of radial distribution channels that conduct a pressure medium to the outer circumference of the shaft 16. The outlet of each channel from the shaft 16 is provided at different heights. A circumferential groove 26 or the like can be provided in the outer circumference of the shaft 16 between the outlets of the transverse channels of a pressure-medium line. The groove 26 delivers the pressure medium in the circumferential direction of the shaft 16 in an unobstructed manner along the groove 26 to the entire outer circumference of the shaft 16 in the area of the groove 26. This enables a fully rotatable pressure-medium supply in all circumferential positions of the rotary device 10, i.e. over 360 degrees.

[0050] The pressure-medium distribution means 17 is in turn located at the outer circumference of the shaft 16 and thus around the shaft 16. It is a sleeve-like cylindrical piece which is coupled to the shaft 16 in a sealed manner but which can rotate freely in the circumferential direction. The distribution means 17, together with the shaft 16 and the circumferential grooves 26 provided in the same for the pressure medium, limits the circumferential annular channels for the pressure medium. In other words, the transverse channels arranged in the shaft 16 respectively connect to their own grooves 26 on the outer surface of the shaft 16, which are collectively designated in Figure 6a as the annular channel system 37. The distribution means 17 has corresponding annular channels 38, which are designated in Figure 6b. The annular channels 38 are connected to the fittings 31, 32 of the distribution means 17 in a manner known per se . Annular seals 71 are provided between the annular channels in a manner known per se (Figure 5) . The distribution means 17 thus includes conduits provided in a known manner for the pressure medium and seals 71 against the shaft 16. The seals 71 separate the circumferential grooves 26 configured in the shaft 16 from one another and seal the distribution means 17 in relation to the shaft 16 at the ends of the shaft 16. The distribution means 17 is positioned in relation to the shaft 16, in particular in relation to the radial channels provided therein and thus also in relation to the circumferential grooves 26 that follow the latter, in such a manner that that the conduits of the distribution means 17 are aligned with the corresponding grooves 26 configured in the shaft 16 at axially corresponding points. This allows the pressure medium to be fed from the groove 26 through the shell of the distribution means 17 to the fittings 31, 32 arranged in the frame 11.

[0051] The distribution means 17 is arranged loosely within the frame 11, and more specifically between the upper transverse support 43 and the lower transverse support 41 of the frame 11. This allows the distribution means 17 to rotate around the shaft 16 together with the frame 11. The pressure medium is conducted from the shaft 16 via the conduits of the distribution means 17 to the fittings 31, 32 provided on the frame casing 12 of the frame 11. Hoses 303 are connected to these fittings. The hoses 303 are provided between the frame 11 and the control valves of the actual tree-handling device 300. The hydraulics are thus connected to the actual tree-handling device 300 via the distribution means 17.

[0052] In the embodiment shown, a lower sliding ring 42 that extends around the shaft 16 is arranged for the distribution means 17. The location of the sliding ring 42 on the shaft 16 and / or the dimensioning of the same in relation to the distribution means 17 are configured to create a play 46.1, 46.2 for the distribution means 17 that allows it to rotate. The distribution means 17 can thus be said to 'float' in the axial direction of the shaft 16. The distribution means 17 is thus fully rotatable between the bearing 25 above it and the sliding ring 42 below it. Below the distribution means 17, the sliding ring 42 is arranged between the shaft 16 and the tapered roller bearing 36.

[0053] The sliding ring 42 can be attached to the shaft 16 by means of (e.g. , 8 - 15) bolts 44. It thus remains in place between the shaft 16 and the extension 45 of the shaft 16. It simultaneously produces the installation conditions, i.e. the play 46.1 and 46.2 of the distribution means 17. The play 46.1 and 46.2 is provided here at both ends of the rotatable distribution means 17.

[0054] Moreover, the rotary device 10 also includes a drive arrangement 55 for rotating the frame 11 relative to the shaft 16. The drive arrangement 55 can be implemented by means of a toothed transmission 56. The drive arrangement 55 includes a first, driven set of teeth 53' arranged in connection with the shaft 16 and a second, driving set of teeth 33' arranged in connection with the drive motor 13 for driving the first set of teeth 53' and thereby rotating the frame 11 relative to the shaft 16.

[0055] In the embodiment shown, by means of the set of teeth 53' on the outer circumference of the gearwheel 53 arranged in the upper part of the rotary device 10, the drive motor 13 rotates, by means of its gearwheel 33, i.e. , driving set of teeth 33' , the entire outer part of the rotary device 10, which outer part is supported by and arranged in connection with the bearing arrangement, relative to the shaft 16 and the distribution means 17. The rotatable outer part includes at least the frame 11 with its transverse supports 41, 43 and the frame casing 12 that join the transverse supports 41, 43. This rotatable frame 11 is connected to the arms 308 or the like, which in turn are connected to the tree-handling device 300. If the rotary motor 13 is connected to the frame 11 in a fixed manner, then it also rotates with the frame 11. In other words, in the embodiment shown, the circular gearwheel 53 provided on the shaft 16 is thus a non-rotating part of the shaft 16, and the gearwheel 33 of the drive motor 13 moves over the teeth 53' of the gearwheel A second bearing 35 is provided in the transverse support 41 of the lower end of the device frame 11. When work is carried out with the tree-handling device 300, which is suspended from the working boom assembly 203 via the rotary device 10, the second bearing 35 bears the tree-handling device 300 attached to the frame 11. It thus also receives the loads caused by the suspension of the tree-handling device 300. The weight of the tree-handling device 300 is consequently borne by means of the bearing arrangement 35 on the shaft 16, the upper part of which includes the attachment bracket 29 of the rotary device 10. It is connected in a conventional manner via the attachment bracket 29 to the base machine 201, for example by means of the link connection .

[0056] In Figures 6a and 6b, the parts that rotate relative to each other are clearly visible. Fixed to the upper end of the shaft 16 is the link bracket 29 by which the rotary device 10 is attached to the working boom assembly 203 via the link, which allows a swaying.

[0057] Figure 5 also shows the installation of the rotary motor 13 in the frame 11 and the driving gearwheel 33 connected to its shaft 30. The gearwheel 33 is supported, for example, by a needle roller bearing 34 on the frame 11.

[0058] The invention relates to a bearing arrangement of a rotary device 10 and to the provision of features that protect the structure of a rotary device 10 by means of the bearing arrangement. The bearing arrangement of the rotary device 10 can be said to include a first bearing 25 and a second bearing 35. The bearings 25, 35 are at a distance from each other in the rotary device 10 and are thus separate. The primary function of the bearings 25, 35 in the rotary device 10 is to enable a rotational movement of the frame 11 of the rotary device 10 around the static shaft 16 that bears the weight of the frame 11 of the rotary device 10. In other words, the frame 11 is thus supported coaxially on the shaft 16 by means of the bearings 25, 35. The bearing arrangement thus bears the axial load exerted on the same by the attached tree-handling device 300 suspended from the rotary device 10. In addition to enabling rotational movement, the bearings 25, 35 also have other functions in the rotary device 10, for example handling different loads. Working with the tree-handling device 300 puts stress on the bearings 25, 35 in the form of different loads and impacts .

[0059] At least one of the bearings is arranged to receive radial forces acting on the rotary device 10. According to one embodiment, this can be the first bearing 25 of the rotary device 10, which is arranged in the upper part of the rotary device 10. In the embodiment shown, this bearing 25 is a ball bearing 27. It is arranged axially underneath the gearwheel 53 connected to the shaft 16 and above the distribution means 17. In the radial direction, the bearing 25 lies between the shaft 16 and the frame 11 here, more specifically within the transverse support 43 of the upper part of the device frame 11. The ball bearing 27 is thus supported by its inner ring 28.1 on the shaft 16 and by its outer ring 28.2 on the frame 11, more specifically on the transverse support 43 of the upper part of the frame 11 (inset of Figure 7) . The first bearing 25 is thus configured to bear the radial forces transmitted from the frame 11 to the shaft 16 at an upper part of the shaft 16.

[0060] One of the bearings is configured to bear the frame 11 axially on the shaft 16. According to one embodiment, this can be the second bearing 35 of the rotary device 10, which can be arranged in the lower part of the rotary device 10. In the embodiment shown, this second bearing 35 is a tapered roller bearing 36.

[0061] The tapered roller bearing 36 can be said to be loaded here.

[0062] The loads acting on the tapered roller bearing 36 thus occur by the force of gravity. In other words, the load acting on the tapered roller bearing 36 is governed by the tree-handling device 300 attached to the rotary device 10, which is suspended from the working boom assembly 203.

[0063] The tapered roller bearing 36 can also be said to not involve a preload. The axial load of the tree-handling device 300 produces the corresponding attribute for the tapered roller bearing 36.

[0064] The tapered roller bearing 36 is configured to act as the sole bearing 35 that bears the frame 11 axially. It is thus also possible to speak of a single bearing 35 in this case. In other words, there is no counterpart to this bearing in the rotary device 10, for example in the form of a second tapered roller bearing, as is often the case with tapered roller bearings 36 in typical applications. The tapered roller bearing 36 can thus be said to be unilaterally supported. This follows from the fact that, when work is performed with the tree-handling device 300, the load on the tapered roller bearing 36 mainly occurs in one direction only. This direction is downwards. The load is produced by the tree-handling device 300 attached to the rotary device 10 from which it is suspended by the force of gravity.

[0065] The tapered roller bearing 36 makes it possible to implement a play 14 in the rotary device 10 that improves the operation and in particular the durability of the rotary device 10 safely and in a manner that improves the stress resistance of structures. In addition to the tapered roller bearing 36 used in the bearing arrangement, the rotary device 10 according to the invention includes an axial play 14 configured between its frame 11 and the shaft 16. The tapered roller bearing 36 makes it possible to implement a small amount of play 14 that nevertheless improves an ability to withstand shocks compared to, for example, the implementation of a thrust ball bearing in the lower part of the rotary device 10 known in the prior art.

[0066] Figures 7 and 8 illustrate the axial movement provided in the rotary device 10 for its frame 11 relative to the shaft 16. In other words, Figures 7 and 8 illustrate the axial play 14 configured in the rotary device 10 for the frame 11 and the corresponding movement. Figures 7 and 8 also illustrate the action of the tapered roller bearing 36 between the frame 11 and the shaft 16 intended to provide this play 14.

[0067] Figure 7 first shows the situation, including an enlargement, of the functional relationship between parts of the rotary device 10, more specifically between its frame 11 and the shaft 11, in connection with the upper bearing 25, i.e. the ball bearing 26 here, when the tree-handling device 300 is used to perform the operations that are typical for it. The treehandling device 300 is thus lifted off the ground into the air by the crane 202. It thus hangs freely at the end of the working boom assembly 203, i.e. from the rotary device 10, and more specifically from the frame 11 of the rotary device 10. The large arrow at the top of the rotary device 10 represents this lifting force caused by the working boom assembly 203.

[0068] In this situation, the upward lifting force produced by the working boom assembly 203 acts on the shaft 16, which the working boom assembly 203 is configured to act on in the rotary device 10. The working boom assembly 203 thus pulls the shaft

[0069] 16 upwards. Thanks to the axial play 14 provided in relation to the frame 11, the shaft 16 is thus raised off the frame 11. More specifically, the gearwheel 53 arranged on the shaft 16 is thus raised off the transverse support 43 of the upper part of the frame 11. These include contact surfaces 60 and 61, wherein the contact surface 60 is provided on the lower surface of the gearwheel 53 and the contact surface 61 is provided on the upper surface of the frame 11, and more specifically on the upper surface of the upper transverse support 43 of the frame 11. The contact surfaces 60, 61 can also be called support structures or impact surfaces. In this situation, the contact surfaces 60, 61 are thus separate. The parts are dimensioned in such a manner that the axial play 14 is, for example, 0.2 - 0.5 mm. More generally, the structure is dimensioned in such a manner that the play 14 can be, for example, approximately 0.05 - 0.8 mm (with a tolerance of +0.1) , more specifically 0.05 - 0.6 mm, and most preferably 0.15 - 0.6 mm. In twisting movements, there additionally occurs a torque in connection with the play 14.

[0070] Moreover, in this normal working condition of the tree-handling device 300, the tapered roller bearing 36, which is arranged in the bottom part of the rotary device 10 and which is borne at its underside by the shaft 16, is pressed against the frame 11 of the rotary device 10. This is caused by the pulling force produced by the tree-handling device 300 attached to the frame 11 of the rotary device 10, because it is suspended in the air. This pressing action is in turn illustrated by the two smaller arrows at the bottom of Figure 7. The tapered roller bearing 36 is thus arranged tightly in its closed position and thus enables a circumferential rotation of the tree-handling device 300 around the shaft 16. Figure 8 in turn shows the situation, including an enlargement, of the relationship between parts of the rotary device 10, here in connection with both the upper and lower bearings 25, 35, in the event of an impact force acting on the rotary device 10 from below. Such an impact force on the rotary device 10 is caused, for example, when the tree-handling device 300 strikes the ground. One can also speak of a negative force acting on the rotary device 10. In this case, the frame 11 of the rotary device 10 is able to move a small distance vertically, i.e. in the axial direction of the rotary device 10, relative to the static shaft 16 connected to the working boom assembly 203. This movement of the frame 11 relative to the shaft 16 is rendered possible by the play 14 arranged between the frame 11 and the shaft 16 in the upper part of the rotary device 10, which is visible in the inset in Figure 7. This play 14 is thus configured to allow the frame 11 to perform an axial movement determined by the play 14 in a situation of an impact acting on the rotary device 10. As the frame 11 and the shaft 16 are overlapping in connection with the play 14, the play 14 between them can be said to be axial. As is conventional, the longitudinal direction of the shaft 16 defines the axial direction .

[0071] In this situation, the downward force caused by the working boom assembly 203 acts on the shaft 16, which the working boom assembly 203 is configured to act on in the rotary device 10. The working boom assembly 203 thus places a downward load on the shaft 16. The large arrow at the top of Figure 8 represents this load. In addition, the opposite impact force caused by the tree-handling device 300 and acting on the rotary device 10 from below when the tree-handling device 300 strikes the ground places an upward load on the frame 11. The frame 11 is thus raised upwards relative to the shaft 16 thanks to the play 14 and the axial play 14 arranged for the frame 11 is closed, as shown in Figure 8. In other words, the frame 11 rises around the shaft 16. The frame 11 and the shaft 16 thus come into contact at the site of the play 14. In other words, the frame 11 touches the shaft 16, i.e. the lower limit 61 of the play 14 and the upper limit of the play 14 make contact.

[0072] More specifically, in the situation shown in Figure 8, the transverse support 43 of the upper part of the frame 11 presses against the gearwheel 53 arranged on the shaft 16. As mentioned above, these include contact surfaces 60 and 61, wherein the contact surface 60 is provided on the lower surface of the gearwheel 53 and the contact surface 61 is provided on the upper surface of the frame 11, and more specifically on the upper surface of the upper transverse support 43 of the frame 11. The contact surfaces 60 and 61 are thus in contact with each other in this situation. The gearwheel 53 and its support on the shaft 16 provide a sufficient support structure to act as an impact surface. The structure thus comes together at a predetermined and consequently set point in the upper part in a situation of an axial impact. This point is selected and formed in terms of its support structure in such a manner that it can withstand loads .

[0073] In addition, in this situation of an impact load, a play is thus in turn formed in connection with the tapered roller bearing 36 arranged in the bottom part of the rotary device 10 and borne at its underside by the shaft 16. The extent of this axial play is at least equal to the play 14 provided in the upper part for the frame 11. This allows the frame 11 to perform the axial movement according to the invention. The relative movement of the shaft 16 and the frame 11 thus occurs in opposite directions. The tapered roller bearing 36 is advantageously used in this connection because it makes it possible to provide the play in question and thus also the movement of the frame 11 in a controlled manner. The support elements 48, 54 and support surfaces arranged in the frame 11 and the shaft 16 for the tapered roller bearing 36 can thus also be said to diverge axially from each other in connection with the tapered roller bearing 36. This is caused by the impact force produced by the tree-handling device 300 attached to the frame 11 when it hits the ground. The fit of the parts in connection with the tapered roller bearing 36 is thus temporarily loose relative to its closed position, which enables the movement of the frame 11 determined by the play 14 first upwards and then back to its closed position.

[0074] Thanks to the play 14 arranged in the rotary device 10 for the frame 11 and the use of a tapered roller bearing 36, the bearings 25 and 35 as well as other structures of the rotary device 10 - such as, for example, its frame 11 - are not loaded, for example, in a situation where the tree-handling device 300 strikes the ground with force. The axial movement between the frame 11 and the shaft 16 at the upper part of the rotary device 10, i.e. at the bearing 25, can be provided, for example, in such a manner that the inner ring 28.1 of the bearing 25 is fixed on the shaft 16 by an interference fit. A small amount of play that allows a mutual axial sliding at the interface designated by the reference number 58 in the inset of Figures 7 and 8 is thus provided between the frame 11, and more specifically the upper transverse support 43 of the frame 11, and the first bearing 25, and more specifically the outer ring 28.2 of the first bearing 25. One can also speak of an axial sliding fit between these parts. The sliding fit 58 is configured to allow the axial movement rendered possible and determined by the play 14. One can thus also speak of a floating fit between the frame 11 and the outer ring 28.2 of the first bearing 25. A small but sufficient axial movement is thus rendered possible between the outer ring 28.2 of the bearing 25 and the part in connection with it, i.e. the frame 11, at the site designated in the inset of Figure 7 by the reference number 14. The axial impact acting on the frame 11 thus does not load the bearing elements 25, 35 or the frame 11. In other words, the frame 11 as a whole, more specifically the transverse support 43 of the frame 11 in connection with the bearing 25, is thus able to move axially in relation to the axially fixed bearing 25, i.e. the bearing 25 attached to the shaft 16, and thus also in relation to the outer ring 28.2 of the bearing 25.

[0075] In order to allow the axial movement of the frame 11, the other parts of the shaft 16 and frame 11 that are arranged contiguously to each other are configured to allow the axial movement produced owing to and determined by the provided play 14. These parts include, for example, the sets of teeth 53' , 33' of the drive arrangement 55. According to one embodiment, the first, driven set of teeth 53' and the second, driving set of teeth 33' are thus gearwheels 53, 33 with straight teeth 53' , 33' in order to allow an axial movement. In addition, the structures configured to allow an axial movement here also include the first bearing 25. With respect to the first bearing 25, reference is made here to the sliding fit of the section 58. The sets of teeth 53' 33' and the first bearing 25 are thus configured to render possible an axial play 14, i.e. the axial movement of the frame 11.

[0076] Thanks to the tapered roller bearing 36 located in the lower part of the rotary device 10, the axial length of the shaft 16 can also be shorter than, for example, in rotary devices of the prior art. This makes the rotary device 10 more compact. This thus makes the shaft 16 more economical in terms of demanding manufacturing methods and raw materials pertaining to the shaft 16. In other words, owing to its shorter length, the shaft 16 requires less raw material as well as less machining. According to one embodiment, a diameter of the shaft 16 can be 35 - 60%, preferably 40 - 52%, of a length of the shaft 16. According to one embodiment, the diameter of the shaft 16 can be, for example, 39 mm and the length 84 mm. The length of the shaft 16 is defined and specified here as the length of the continuous, i.e. monolithic, part of the shaft 16, without the extension 45. The diameter of the shaft 16 is in turn defined and specified at the location of the distribution means 17.

[0077] In the embodiment shown, the tapered roller bearing 36 is arranged on the extension 45, which is attached to the end of the shaft 16 in a detachable manner. The extension 45 can be implemented, for example in relation to the shaft 16, with more economical manufacturing methods and raw material requirements.

[0078] A play 14 is provided between the gearwheel 53 and the frame 11, and more specifically the upper transverse support 43 of the frame 11, as shown in Figure 7. The play 14 between the gearwheel 53 and the frame 11 is adjusted, for example, during the manufacturing and / or assembly of the parts. It is possible to further increase the play 14 during assembly, for example by placing spacing rings (s = 0.1 - 0.3 mm) between the bearing 35 of the lower part and the extension 45 of the shaft 16, i.e. at the point 57 shown in Figure 8, underneath the inner ring 18 of the tapered roller bearing 36. As mentioned above, the play 14 can be, for example, in the range of 0.1 - 0.7 mm, more specifically 0.2 - 0.5 mm. A functional lubrication between the gearwheel 53 and the transverse support part 43 of the upper part of the frame 11, i.e. the upper flange of the frame 11, is thus still achieved by the lubrication of the gearwheel 53.

[0079] A bearing housing 47 of the tapered roller bearing 35 is provided above the tapered roller bearing 36 and below the monolithic part of the shaft 16, i.e. below the part that includes the distribution channels. The bearing housing 47 can be attached to the frame 11, for example, with bolts 49. It is thus connected to the transverse support 41 of the lower part of the frame 11, i.e. to the lower flange of the frame 11. On the other hand, the bearing housing 47 could also be integrated directly into the part 11, i.e. into the transverse support 41 of the lower part of the frame 11, if the assembly of the rotary device 10 allows it. The bearing housing 47 above the tapered roller bearing 36 is connected to the frame 11, so that it is configured to move together with an axial movement of the frame 11. The distance of this movement is at least equal to the play 14 provided in the assembly for the frame 11 in the axial direction of the rotary device 10.

[0080] The outer ring 19 of the tapered roller bearing 36 is configured to bear the frame 11. This occurs via the bearing housing 47 arranged in the frame 11 for the tapered roller bearing 36 above the tapered roller bearing 36. The bearing housing 47 is arranged in contact with the outer ring 19 of the tapered roller bearing 36.

[0081] The tapered roller bearing 36 between the frame 11 and the shaft 16 is arranged to allow a free axial movement, for example in order to protect the bearings 25, 35 and generally the structures of the rotary device 10 from impact forces. According to a first embodiment, the outer ring 19 of the tapered roller bearing 36 can be fixed in the bearing housing 47, more generally in the frame 11, by an interference fit. The axial movement of the frame 11 in connection with the tapered roller bearing 36, which axial movement is required for the function of the play, is achieved by the axial movement of the outer ring 19 of the tapered roller bearing 36. In other words, the outer ring 19 thus moves together with the bearing housing 47 configured in the frame 11. The outer ring 19 of the tapered roller bearing 36 thus rises by the extent of the play 14 in an impact situation. When an axial movement occurs, the bevelled tapered surface (reference number 59 in Figure 6a) of the tapered roller bearing 36 still supports the structure laterally throughout the movement. The movement of the outer ring 19 of the tapered roller bearing 36 could be even greater because of its tapered structure, but it is limited by the extent of the play 14 provided in the upper part of the frame 11, i.e. the distance between the contact surfaces 60, 61 in the suspended condition of the tree-handling device 300.

[0082] According to a second embodiment, an axially sliding fit can be provided between the bearing housing 47 of the tapered roller bearing 36, i.e. in more general terms the frame 11, and the outer ring 19 of the tapered roller bearing 36. In this case, the axial movement of the frame 11 in connection with the tapered roller bearing 36 occurs between these parts 47 and 19. In this case, the outer ring 19 of the tapered roller bearing 36 does not move in the axial direction.

[0083] Figure 9 shows an oblique view from above of an assembled rotary device 10, but without the cover of the top part. Both the fixed gearwheel 53 and the driving gearwheel 33 of the drive motor 13 that rotates the frame 11 are thus visible. Figure 10 shows a corresponding oblique view of the rotary device 10 shown in Figure 9 from below. The tapered roller bearing 36 provides the rotary device 10 with a play 14 that improves its durability. The play 14 can be implemented so that it is small but still sufficient to improve an ability to withstand loads. In addition, a further advantage of the tapered roller bearing 36 is that it can receive both axial and radial forces. The tapered roller bearing 36 itself and, moreover, the overall structure of the rotary device 10 are thus better able to withstand both axial stresses - such as, for example, impacts - and radial stresses - such as, for example, twisting movements. Although the play 14 formed in the structure is small, it is still sufficient to enable, for example, a (non-abrasive) rotational movement between the parts and to receive axial and radial impacts and torsional forces acting on the structure in a manner that puts less stress on the structures. In a situation where, for example, the treehandling device 300 hits the ground with force, the structure of the rotary device 10 yields in a controlled and predetermined manner thanks to the play 14 provided therein and consequently also withstands the forces caused by the stresses in question better. The provided play 14 and the tapered roller bearing 36 also allow the bearing 25 in the upper part of the rotary device 10 - which is implemented, for example, as a ball bearing 27 - to also twist slightly, which also contributes to the durability of the structure and helps to provide a more compact structure. Compared to a thrust ball bearing, for example, the tapered roller bearing 36 enables the play according to the invention as well as a twisting movement.

[0084] A characteristic feature of the tapered roller bearing 36 is its taper angle. According to a variant, this angle can ne understood as the angle of the raceway of the outer ring 19 of the tapered roller bearing 36. In the solution according to the invention, the angle of the tapered roller bearing 36 can be very slight, i.e. small. For instance, it can be 5° - 20°, more specifically 6° - 18°, and most preferably 7° - 14°, measured in relation to the vertical or axial direction and as a downward facing angle. As the angle is slight, the roller elements, i.e. the tapered rollers 52, are in turn quite steep in the assembly, i.e. they are only slightly inclined towards the shaft 16. The rollers 52, and thus also the tapered roller bearing 36, are arranged in the assembly in such a manner that the rollers 52 are closer to the shaft 16 at their upper ends than at their lower ends. I.e. , the axial load borne by the tapered roller bearing 36 is oriented downwards. In the solution according to the invention, a sufficient axial load-bearing capacity can even be achieved with the slightest angles of tapered roller bearings 36 available on the market. A specific example of a suitable tapered roller bearing 36 is, for example, NSK HR32917J. In this case, the inner diameter of the bearing is 85 mm, the outer diameter is 120 mm, and the axial length of the bearing is 23 mm. The rollers 52 are known tapered revolving elements. Their cross-section tapers towards the inner ring 18 of the bearing 36. The inner diameter of the bearing 36 can be configured in such a manner that, for example, a possible electrical connector element can be accommodated in the arrangement.

[0085] The tapered form of the tapered roller bearing 36 also provides good radial support in a normal working situation. It thus provides a load-bearing capacity in both directions. A same, i.e. , good radial support is also achieved in an impact situation, i.e. , for example, when the outer ring 19 of the tapered roller bearing 36 rises. This is due to the slight angle of the tapered roller bearing 36 used. There is thus only a slight loss of radial support. The tapered shape that is characteristic of the structure of the tapered roller bearing 36, more specifically of the inner ring 18 and the outer ring 19 belonging to the tapered roller bearing 36, enables an axial movement of the outer ring 19 relative to the rollers 52 and inner ring 18 nested inside it in the situation of an axial load. When axial impact forces from below are encountered, the outer ring 19 can rise upwards by the distance allowed by the play 14 arranged in the structure. Analogously, after the impact, it descends back into place behind the rollers 52 and their retainer, i.e. back into the nested assembled configuration with the inner ring 18. This way, when axial forces from below are encountered, the tapered roller bearing 36 is not loaded in the same way as, for example, a thrust bearing. In general, it can be said that the assembly including the tapered roller bearing 36 is configured to allow a movement of the extent of the play 14 in order to protect the structure - such as, for example, the bearings 25, 35 and the frame 11, as well as the shaft 16 - from impact forces. In addition, the tapered roller bearing 36 receives and in particular withstands radial forces better than, for example, a thrust ball bearing known from the prior art.

[0086] A special and even anomalous feature of the use of a tapered roller bearing 36 in a rotary device 10 in accordance with the invention is that it does not require a conventional preloading characteristic of tapered roller bearings 36, as is the case, for example, in many other typical applications. The tapered roller bearing 36 also surprisingly acts here as a substitute for a thrust bearing, i.e. it is arranged transversely in the rotary device 10. Its axial direction is thus vertical. The load caused by the tree-handling device 300 suspended from the rotary device 10 is thus distributed evenly over its entire annular roller raceway in a manner characteristic of thrust bearings. In other words, the load can be said to be symmetrical .

[0087] The tree-handling device 300, when it is suspended from the rotatable, load-bearing part of the rotary device 10, i.e. from the frame 11, pulls the frame 11 downwards. The upper shoulder structure 48 configured in the bearing housing 47 of the tapered roller bearing 36 thus loads the tapered roller bearing 36 here against the end shoulder structure 54 of the extension 45, more generally of the shaft 16, i.e. for all practical purposes against the shaft 16. In other words, the inner ring 18 of the tapered roller bearing 36 is configured to be borne on the shaft 16. More specifically, in the embodiment shown, this is achieved by means of the load-bearing shoulder structure 54 configured in the shaft 16, by which the inner ring 18 of the tapered roller bearing 36 is configured to be borne in connection with the shaft 16. According to one embodiment, the load-bearing shoulder structure 54 can be configured in the extension 45 belonging to the shaft 16. The shaft 16 in turn includes the shoulder structure 48 configured in the bearing housing 47 for the outer ring 19 of the tapered roller bearing 36 that is configured to bear the frame 11. When the tree-handling device 300 hits the ground, the structure yields thanks to the play 14 and is not subjected to as much stress. This is made possible by the axial movement of the frame 11 that occurs in connection with the tapered roller bearing 36 according to the play 14 configured in the upper end of the shaft 16 when such impacts are encountered.

[0088] According to one embodiment, the rotary device 10 according to the invention can be equipped with a urea treatment capability with or without corresponding conduits (not shown) . It is thus also possible for the tapered roller bearing 36 to be fitted in accordance with the invention in rotary devices 10 that may or may not include a system for conveying an auxiliary substance, such as, for example, urea, through the rotary device 10 to a designated destination. It is additionally possible to use a tapered roller bearing 36 in a bearing arrangement of a rotary device 10 in applications with ducts for cables for electrics and / or data communications. It is consequently also possible to use the tapered roller bearing 36 in accordance with the invention in rotary devices 10 with a wired system for conducting electricity, such as, for example for electric power and / or for an electronic control system, via the rotary device 10, as well as in rotary devices 10 without one or either of these functions. In the absence of such a system, the electric power required, for example by the valves of the tree-handling device 300, can be generated in the harvester head itself, for example using a hydraulically operated electric generator. Analogously, electronic control signals for controlling the valves can be emitted (and received) by means of, for example, a wireless data transfer.

[0089] The invention has been explained in the foregoing as an embodiment in which the upper bearing 25 is a ball bearing 27 that receives radial forces and the lower bearing 35 is a tapered roller bearing 36 that bears axial forces and also withstands radial forces. It is noted that it is equally possible to arrange the bearings in the rotary device 10 the other way round. In this case, the tapered roller bearing is in the upper part of the rotary device 10 and the radial bearing is in the lower part of the rotary device 10. The axial play would remain unchanged. In addition, for example instead of a ball bearing 27 being arranged in the upper part, the upper bearing 25 could also be, for example, a plain bearing, a second tapered roller bearing or any other bearing capable of withstanding radial forces.

[0090] In the described embodiment, the parts belonging to the drive arrangement 55 are configured in such a manner that the drive motor 13 and the driving set of teeth 33' arranged on it are installed in the frame 11. They are thus on the outside of the driven set of teeth 53' when the sets of teeth 53' , 33' are implemented as gearwheels 53, 33. The implementation according to the invention, i.e. the utilization of a play 14 to improve the ability of a rotary device 10 to withstand loads, is not limited to this embodiment, however, but the drive arrangement can also be of different kind. One example of such an arrangement could be one in which the drive motor and the driving set of teeth arranged thereon are installed coaxially with respect to the driven set of teeth.

[0091] In addition to a rotary device 10, the invention also relates to a tree-handling device 300. The tree-handling device 300 includes gripping means 305' for gripping a tree 400 for a cutting operation; a blade function preferably configured on at least a part of the gripping means 305' for delimbing a tree 400 of branches; a feeding device 304 for delimbing a tree 400 by means of the cutting function and / or for cutting a tree 400 into logs; a cutting device 301' for cutting a tree 400, and a felling mechanism 307 for changing the position of the treehandling device 300 between a felling position and a delimbing position. The tree-handling device 300 is equipped with a rotary device 10 according to the invention.

[0092] A still further object of the invention is a tree-harvesting machine 200. The tree-harvesting machine 200 includes a motorized base machine 30; a crane 202, which is arranged on the base machine 30 and equipped with a working boom assembly 203; and a tree-handling device 300 arranged at the end of the working boom assembly 203. The tree-handling device 300 includes gripping means 305' for gripping a tree 400 for a cutting operation; a blade function preferably configured on at least a part of the gripping means 305' for delimbing a tree 400 of branches, a feeding device 304 for delimbing a tree 400 by means of the blade function and / or for cutting a tree 400 into logs; a cutting device 301 for cutting a tree 400; a felling mechanism 307 for changing the position of the tree-handling device 300 between a felling position and a delimbing position. The tree harvesting machine 200 is equipped with a rotary device 10 according to the invention.

[0093] The invention has been described in the foregoing without, for example, a urea supply, a power supply, or a control-signal transmission. In addition, the conveyance of a pressure medium via the rotary device 10 was described by reference and without reference to the drawings. With regard to all these aspects, reference is made, for example, to international patent application publication no. WO 2019 / 193255 of the Applicant. This document discloses a way in which all these aspects can also be implemented in a rotary device 10 according to the invention .

[0094] It is understood that the foregoing description and associated figures are intended solely to illustrate the present device and method according to the invention. The invention is therefore not limited to the embodiments described in the foregoing or defined in the claims, but rather many different variants and modifications of the invention will be apparent to those skilled in the art that are possible within the scope of the inventive idea as defined by the attached claims.

Claims

CLAIMS1. A rotary device for a tree-handling device, wherein the rotary device includes- a shaft (16) configured to be suspended from a boom arm (204) ,- a frame (11) supported coaxially on the shaft (16) by means of bearings (25, 35) , wherein the bearings (25, 35) include a first bearing (25) configured to bear radial forces transmitted from the frame (11) to the shaft (16) and a second bearing (35) configured to bear the frame (11) axially on the shaft (16) ,- a drive arrangement (55) for rotating the frame (11) relative to the shaft (16) , wherein the drive arrangement (55) includes a first, driven set of teeth (53' ) arranged in connection with the shaft (16) and a second, driving set of teeth (53' ) arranged in connection with the drive motor (13) for driving said first set of teeth (53' ) and rotating the frame (11) relative to the shaft (16) ,- pressure-medium distribution means (17) between the shaft (16) and the frame (11) as well as first fittings (21, 22) on the side of the shaft (16) and second fittings (31, 32) on the side of the frame (11) that are connected to said distribution means (17) , characterized in that- the said bearing (35) that is configured to bear the frame (11) axially is a loaded tapered roller bearing (36) without a preloading that is configured to act as the sole bearing that bears the frame (11) axially,- the tapered roller bearing (36) includes an inner ring (18) and an outer ring (19) , wherein the inner ring (18) is configured to be borne by the shaft (16) and the outer ring (19) is configured to bear the frame (11) ,- an axial play (14) is configured between the frame (11) and the shaft (16) , which axial play (14) is configured to allow the frame (11) to perform an axial movement determined by the play (14) in a situation of an impact acting on the rotary device (10) ,- the sets of teeth (53' , 33' ) of the drive arrangement (55) and the first bearing (25) are configured to allow said play ( 14 ) .

2. The rotary device according to Claim 1, characterized in that- the first bearing (25) that is configured to bear radial forces transmitted from the frame (11) to the shaft (16) is arranged in an upper part of the shaft (16) ,- the second bearing (35) , which is said tapered roller bearing (36) and which is configured to bear the frame (11) axially on the shaft (16) , is arranged in a lower part of the frame (11) .

3. The rotary device according to Claim 1 or 2, characterized in that an axial sliding fit (58) is provided between the frame (11) and the first bearing (25) .

4. The rotary device according to any one of Claims 1 to 3, characterized in that the distribution means (17) is rotatable.

5. The rotary device according to any one of Claims 1 to 4, characterized in that the tapered roller bearing (36) between the frame (11) and the shaft (16) is configured to allow said axial movement rendered possible by the play, for example to protect the bearings (25, 35) from impact forces.

6. The rotary device according to any one of Claims 1 to 5characterized in that a bearing housing (47) is configured in the frame (11) for the tapered roller bearing (36) , wherein the bearing housing (47) is arranged in contact with the outer ring (19) of the tapered roller bearing (36) .

7. The rotary device according to any one of Claims 1 to 6, characterized in that a bearing housing (47) is configured in the frame (11) for the tapered roller bearing (36) , wherein the bearing housing (47) is configured to move together with the frame (11) in the axial direction of the rotary device (10) by a distance that corresponds to the provided play (14) .

8. The rotary device according to any one of Claims 1 to 7, characterized in that an axial sliding fit is provided between the frame (11) and the outer ring (19) of the tapered roller bearing (36) to provide an axial movement of the frame (11) .

9. The rotary device according to any one of Claims 1 to 7, characterized in that an interference fit is provided between the frame (11) and the outer ring (19) of the tapered roller bearing (36) , and said axial movement of the frame (11) is configured to be provided by an axial movement of the outer ring (19) of the tapered roller bearing (36) .

10. The rotary device according to any one of Claims 1 to 9, characterized in that the shaft (16) includes a load-bearing shoulder structure (54) on which the inner ring (18) of the tapered roller bearing (36) is configured to be borne in connection with the shaft (16) .

11. The rotary device according to any one of Claims 1 to 10, characterized in that the shaft (16) includes an extension (45) on which said load-bearing shoulder structure (54) is configuredto bear the inner ring (18) of the tapered roller bearing (36) in connection with the shaft (16) .

12. The rotary device according to any one of Claims 1 to 11, characterized in that a lower sliding ring (42) that extends around the shaft (16) is arranged for the distribution means (17) , wherein the location of said lower sliding ring (42) on the shaft (16) and / or the dimensioning of the same in relation to the distribution means (17) is configured to create a play (46.1, 46.2) for the distribution means (17) that allows it to rotate .

13. The rotary device according to Claim 12, characterized in that the sliding ring (42) is arranged between the shaft (16) and the tapered roller bearing (36) .

14. The rotary device according to Claim 12 or 13, characterized in that the sliding ring (42) is arranged between the shaft (16) and the extension (45) of the shaft (16) .

15. The rotary device according to Claim 14, characterized in that the sliding ring (42) is configured to be attached to the shaft (16) between the shaft (16) and the extension (45) of the shaft (16) by a bolt fastening (44) .

16. The rotary device according to any one of Claims 1 to 15, characterized in that the tapered roller bearing (36) is arranged on the extension (45) belonging to the shaft (16) , wherein the extension (45) is attached to the end of the shaft (16) in a detachable manner.

17. The rotary device according to any one of Claims 1 to 16, characterized in that the first bearing (25) that is configuredto bear radial forces transmitted from the frame (11) to the shaft (16) is a ball bearing (27) arranged on an upper part of the shaft (16) .

18. The rotary device according to any one of Claims 1 to 17, characterized in that the taper angle of the tapered roller bearing (36) is 5 - 20 degrees, more specifically 6 - 18 degrees, most preferably 7 - 14 degrees.

19. The rotary device according to any one of Claims 1 to 18, characterized in that the first, driven set of teeth (53' ) and the second, driving set of teeth (33' ) are gearwheels (53, 33) with straight teeth (53' , 33' ) .

20. The rotary device according to any one of Claims 1 to 19, characterized in that- the rotary device (10) includes a member (29) which is arranged on the upper part of the rotary device (10) and which is configured to fasten the shaft (16) and the gearwheel (53) to each other by means of a first bolt fastening (39.1) arranged on the outside of the end (15) of the shaft (16) ,- the end (15) of the shaft (16) is configured to overlap with the gearwheel (53) in the centre bore of the gearwheel (53) ,- the link bracket (29) is attached to the end (15) of the shaft (16) by means of a second bolt fastening (39.2) in order to eliminate eccentric loads.

21. The rotary device according to any one of Claims 1 to 20, characterized in that a diameter of the shaft (16) is 35 - 60%, preferably 40 - 52%, of a length of the shaft (16) .

22. The rotary device according to any one of Claims 1 to 21, characterized in that the tapered roller bearing (36) is unilaterally supported.

23. The rotary device according to any one of Claims 1 to 22, characterized in that the rotary device (10) includes contact surfaces (60, 61) configured in connection with the frame (11) and the shaft (16) for receiving forces caused in connection with the movement of the frame (11) enabled by said play (14) .

24. The rotary device according to any one of Claims 1 to 23, characterized in that the shaft (16) includes a shoulder structure (48) for the outer ring (19) of the tapered roller bearing (36) that is configured to bear the frame (11) , wherein the shoulder structure (48) is configured in the bearing housing (47) arranged in the frame (11) .

25. The rotary device according to any one of Claims 1 to 24, characterized in that the drive motor (13) and the driving set of teeth (33' ) arranged thereon are installed in the frame (11) on the outside of the driven set of teeth (53' ) .

26. The rotary device according to any one of Claims 1 to 24, characterized in that the drive motor and the driving set of teeth arranged thereon are installed coaxially in relation to the driven gear.

27. A tree-handling device, which includes- gripping means (305' ) for gripping a tree (400) for a cutting operation,- a blade function preferably configured on at least a part of the gripping means (305' ) for delimbing a tree (400) of branches,- a feeding device (304) for delimbing a tree (400) by means of the blade function and / or for cutting a tree (400) into logs,- a cutting device (301' ) for cutting a tree (400) ,- a felling mechanism (307) for changing the position of the tree-handling device (300) between a felling position and a delimbing position, characterized in that the tree-handling device (300) is equipped with a rotary device (10) according to Claim 1.

28. The tree-handling device according to Claim 27, characterized in that the rotary device (10) is a rotary device according to one or more of Claims 2 to 26.

29. A tree-harvesting machine, which includes- a motorized base machine (30) ,- a crane (202) , which is arranged on the base machine (30) and equipped with a working boom assembly (203) ,- a tree-handling device (300) arranged at the end of the working boom assembly (203) , which includes- gripping means (305' ) for gripping a tree (400) for a cutting operation,- a blade function preferably configured on at least a part of the gripping means (305' ) for delimbing a tree (400) of branches,- a feeding device (304) for delimbing a tree (400) by means of the blade function and / or for cutting a tree (400) into logs,- a cutting device (301' ) for cutting a tree (400) ,- a felling mechanism (307) for changing the position of the tree-handling device (300) between a felling position and a delimbing position,characterized in that the tree-harvesting machine (200) is equipped with a rotary device (10) according to Claim 1.

30. The tree-harvesting machine according to Claim 29, characterized in that the rotary device (10) is a rotary device according to one or more of Claims 2 to 26.

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