The object of the invention is a tree harvesting machine, as well as a fully rotating rotary actuator of a harvesting or felling head, which includes

• an axle to be suspended from a boom

• a frame supported by means of bearings on the axle,

• a first driven gear arranged coaxially with the axle,

• a second driver gear and a motor installed in the frame that rotates the driver gear in order to drive the so- called first gear and in order to rotate the frame with respect to the axle,

• rotatable hydraulic oil distribution means between the axle and the frame, said distribution means being con nected to first couplings on the side of the axle and sec ond couplings on the side of the frame.

Here, fully rotating means a construction with unrestricted ro tation .

Between the arm of the tree harvesting machine or multi-pro- cessing machine and the actual harvester head is a rotary actu ator or rotator above the felling device. The felling or tilt ing device is a shank attached to the rotator, the shank being articulated at its bottom with the frame of the harvester head and designed to be driven by means of a hydraulic cylinder in order to pivot the harvester head into an upright position in order to fell the tree or into a horizontal position for de- limbing and sectioning. The device allows the free suspension of the felling head. A felling device is a device, most fre quently simply arms, with which the harvester head can be placed in the felling position by the force of a hydraulic cyl inder. The top part is in turn attached via the rotary device or rotator to the arm of the base machine by means of a so- called universal joint. A rotary movement is thus produced be tween the harvester head and the arm by means of the rotary de vice. The orientation of the axle during the rotary movement is generally vertical with a deviation of approx. ± 30° from the vertical position. The universal joint in the upper part of the rotary device facilitates the positioning of the harvester head in a suspended position. The speed of the rotary device is ap prox. 30r/m ± 50 %. Hydraulic oil is needed in the harvester head for its actuation; moreover, electric power is needed for the actuation of the valves and for data transmission. The pressure of the hydraulic oil is 250 bar ± 30 %, while its flow volume is - 200 1/min ± 30 %. Naturally, a return oil line for the corresponding flow volume is also required, but the pressure here is only ~ 20 bar ± 30 %. Sometimes a part of the return oil can be carried along its own line. This part is formed from the oil leaking from the motors and valves.

Thus, 2 or 3 lines are required for the hydraulic fluids. All electric power and data transfers can be carried with one ap prox. 10 mm cable ± 30 %. These days, all of these operations can be carried out via passageways of freely rotating rotary devices available on the market. In this case, one speaks of so-called fully rotating rotary devices. The most common way is currently, however, to run the hydraulics and electricity past the rotary device directly with tubing. In this case, the lim ited action of the harvester head is a problem. The operator constantly has to be careful not to rotate the harvester head too much so as to avoid damaging the tubing. In practice, de pending on the pliability of the flexible tubing, the angle of rotation is merely approx. ± 180° ± 30 % around the verti cally oriented axle.

In the entire world, approximately 4000 harvester head units (2018) are produced, said harvester heads coming in several different sizes. Only medium-sized harvester heads are made in large quantities (2000 units/year) . The rotary device itself is a separate device. It is difficult to develop integrated rotary motors when the production quantities are small and there are also several sizes. When a separate motor is used with an ex ternal gear train, the same hydraulic motor can be used in large (2 units/machine) and small machines. The necessary mo ment of the rotary device can be achieved with a separate motor that creates a torque of 300 Nm. The 2000 Nm torque of a large machine can be easily achieved with two small motors and a gear ratio of 3.5, wherein the load of the gear is divided between the two gears . With a separate motor the same components can be used in all size classes.

While the final rotational speed in large machines is a maximum of 0.3 r/s, it is 0.6 r/s in small machines and the power de mand is roughly the same in rotary devices of different sizes. Based on these theoretical values, the rate of rotation of the separate motor during rotation is 1 r/s, i.e. 60 r/min, while the power demand is 2kW.

A problem with a freely, fully rotating rotary device is the large amount of space it requires. This is a drawback in par ticular in felling harvester heads. Generally, so-called ring bearings are used. This kind of bearing structure is both sim ple and compact. The bearing is able to take forces as well as moments directed upwards and downwards. Also required for rota tion is a hydraulic motor that causes the rotation of either a chain ring or a ring gear. A rotation occurs in the latter in order to reduce the size of the hydraulic motor so as to achieve a gear ratio of at least 3 or even 6. Moreover, the ac tual passageway section in the device is not subjected to mo ments or other forces, but rather only to the stresses particu lar to the passageway. In new applications, however, a passage way is also needed in summertime for the processing of stumps.

A substance tank and pump are located on the base machine. When the substance is e.g. urea, the dangerous nature of this addi tive for the hydraulics must be taken into account. The pas sageway must be created in such a way that it ensures that the oil and urea are kept separate during operation and mainte nance .

A felling end rotary actuator predominantly in accordance with the introductory part of this application is known from Finnish patent FI75471 (Neva-Kone Oy) . There, the axle suspended from the universal joint is mounted in bearings in the frame sec tion, which is in the upper end of the arm. The frame section includes a gear train that drives the gear of the axle.

Passageways required for hydraulic drive and rotatable distri bution devices are known. The publication WO2014/133399 A1 (Wa- ratah) describes a solution for distributors of hydraulic drive and also includes a rotatable electrical connection that runs through the axle. A corresponding solution can also be found in the publication US 7,735,530 (Puma, LLC) .

The object of the invention is to provide a new design for a rotary device, by means of which it is possible to convey pro cessing fluid, in particular corrosive fluid, from the tank of the base machine to the felling head or for a corresponding ap plication. The distinctive features of the fully rotating ro tary device according to the invention are described in claim 1.

In the freely rotating rotary device according to the inven tion, a passageway for urea or corresponding substance has been accommodated, while its overall structure is cheaper and smaller. The axle fits advantageously into the smaller struc ture and in particular into the smaller diameter by mounting the same in bearings in a new way. Simultaneously, simple bear ing mounts and the possibility of connecting a larger gear (chain or toothed) of the rotary device to a small-flanged axle render the manufacture of a small blank axle possible. The driven large gear (or large chain gear) is in the axle of the rotary device and the driving small gear (chain gear) is in the frame of the rotary device. In itself it is surprising that a non-coaxial rotational solution, bearing mount and additive fluid feed are combined. Especially if an electrical energy passageway through the axle is also implemented.

While the electricity distributor is co-axial and also has a hole running through it, the line most difficult to move, i.e. the processing fluid line for urea, etc. is at the co-axial centre, the feeding of urea occurring with a tube, advanta geously with a hose, at the end of which is a rotatable con nector. In principle, the auxiliary fluid feed line can be used for other applications as well. In one variant, high-pressure hydraulic oil is conducted with a central tube or merely by means of a conduit through the axle and subsequently with a hose or tube through the electricity distributor.

The fully rotating connector for the additional fluid line is ideally beneath the electricity distributor, the tube of the additive fluid conduit being guided to said connector through the electricity distributor. In case the connector for the fluid is above the electrical distributor or inside the axle, the tube to be removed from the connector would be guided through the electricity distributor. Although this design would be possible, it is difficult to realize in practice. Potential leakage would be very problematic for the electricity distribu tor .

The invention is described in the following by means of exam ples and with reference to the attached figures, which illus trate a rotary device in a multi-purpose machine according to the invention.

Figure 1 shows a multi-purpose machine together with a small excavator . Figure 2 shows a rotary device in accordance with the inven tion .

Figures 3a - 3b show an arm of the multi-purpose machine

equipped with a further rotating device in accordance with the invention.

Figures 4a and 4b show the rotating parts of the rotating de vice shown in Figure 3a and their interaction.

Figure 5 shows a section of the rotary device in the plane of the motor.

Figure 5b shows a section of the rotary device perpendicular to the plane shown in Figure 5a.

Figure 1 shows an example of a multi-purpose machine at a sche matic level obliquely from the side. The tree-processing device of the multi-purpose machine, here harvester machine 35, is generally suspended from the base machine 37, here from the ex cavator's working arms 50. The latter comprises arms 52 and 53, wherein the end of the last arm, i.e. the end of the arm 53 here, has an adapter 57, from the joint of which a tree-pro- cessing device 35 is suspended (universal joint with its part 231) . The articulation of the tree-processing device 35 with the arm 53 can be realized, e.g., according to the state of the art with two crossed swivel joints oriented in different direc tions with respect to one another, most frequently with an ar ticulated coupling.

Between the tree-processing device 35 and the articulated cou pling 231 is a rotary actuator (rotator) according to the in vention integrated into an arm 42 of the felling device

(filter) . By means of the rotation device, the tree-processing device 35 can be freely rotated around the axis of rotation of the rotation device. The hydraulic medium flow required by the operational devices (e.g. saw motor 38) of the tree-processing device 35 as well as electricity and processing fluid (gener ally UREA) can be conducted from the base machine 37 via the working arms 50 by means of tubes, most frequently by means of hydraulic medium lines and cables.

The rotary actuator can be designed to be attached with sepa rate components, e.g. with bolts, to the upper end of the arm.

The base machine 37 is equipped, e.g., with wheels or with cat erpillar tracks 371 as shown in Figure 1. It can be said that the tree-processing device includes an operational unit, for example a felling head, the basic parts of which are a felling device 45, a cutting device 38, a feeding device 36 and delimb- ing blades which act as grapplers . The base machine 37 can be wheel-based or equipped with caterpillar tracks 371, as is the case here.

According to a first embodiment shown in Figure 2, the top part of the felling device 45 includes a rotary device, the bottom part of which or frame 4 is integrated into the top part of the arms 42. The top end 43 of the frame 4 is attached via radial bearings 5 and the support elements 41 are supported by thrust bearings 15. The top end 43 and the support elements 41 are fastened securely to the arm 42. That is to say that parts 43 and 41 are attached between the arms 42. An axle 1 is attached to a hanger 2 by means of bolts 9 (as many as 30 units) and a gear 3. The bolts 9 tighten the gear 3 and the axle 1 together by means of a flange 11. A small shoulder structure in the flange 11 is sufficient here. Figure 2 shows apertures 21 ^' and 22' for the connectors. Oil flows via the aperture 21' and fur ther through the connector 212 at the lower surface of element 2 via the conduit 21 formed in the axle 1 and from there fur ther through the rotatable distributor 7 to the connector 211.

The conduit 21 first runs axially in the axle and then exits transversely at point 213. In between is the distributor 7, which comprises passageways and seals 71 for the hydraulic oil, the passageways and seals 71 being made in a known manner.

Element 7 interlocks loosely with the arm 42 and with the upper end 43. In order to avoid that the element 7 rotate together with the axle 1, the tubing in the connectors 211 and 221 is often sufficient for interlocking. The tubes run between the bottom part 4 of the felling head of the harvester head and the control valves of the actual harvester head. By means of the teeth on the outer ring of the gear 3, the hydraulic motor 13 rotates, by means of the gear 33, the entire upper part of the rotary device, which includes, inter alia, elements 1, 3, 2,

202, 231, 14, 16 201, as well as the ring element 151 beneath the bearing 15 and the outer element 194 of the electricity distributor 19. Element 231 is the upper joint of the universal joint on the side of the boom, the upper joint being connected in an articulated fashion to the hanger 2 in the brackets 29 by means of a pin 23. Other typical joints can also be used here which transmit the moment while allowing a swinging in the hor izontal plane.

The bearing 5 is between the axle 1 and the upper end 43. The outer dimensions of the bearing 5 are advantageously greater than those of the element 7. The bearing 5 is only subjected to lateral forces and can move slightly in the direction of the axle 1. Via the aperture in the bearing 5, the entire rotary device can be assembled or disassembled together with the dis tributor 7 and the element 14 initially underneath the upper part 43 between the supports 41, after which a thrust bearing 15 is mounted, to the underside of which a ring nut 16 is screwed. There thus exists a suitable clearance to the gear 3 when the felling device 45 is raised from the hanger 2.

In a state of assembly, the axle 1 is attached to the gear 3 and the hanger 2. Between the axle 1 and the hanger 2 is a seal (at least 2 units) for the hydraulic conduits, e.g. 212. The bolts 9 can now be mounted and tightened for operation. Next, the bearing 5 as well as a glide ring 6 are mounted on the axle 1. The glide ring 6 prevents the element 7 from rubbing the bearing 5. Now the element 7 with its seals is fit onto the axle. There are at least 3 seals 71. By means of a known tech nique, a connection is now created from the conduit 21 to the connector 211 and analogously from the conduit 22 to the con nector 221. Next, the glide ring 12 is mounted so that the ele ment 7 is now between two glide rings (elements 6 and 12) . The lower casing 14 is attached to the axle 1 in the direction of the axle 1 with bolts 18. There are several bolts 18. Element 141 is the shoulder structure in element 14 and the shoulder structure 141 keeps the element 7 in place with a small clear ance with respect to the axle 1. The aperture 22' running from the element 2 to the connector 221 via the conduit 22 functions in the same way as the oil flow from the aperture 21' to the connector 211 via the conduit 21.

In an assembled state, the element 14 extends through the sup port element 41. The frame 4 is integrated between the arms 42. The support element 41 comprises a butt bearing 15 and an ap propriate clearance can be set between the gear 3 and the frame 4 by means of the ring nut 16. During operation, the bearing 15 is subjected to the loads resulting from suspension of the har vester head. Advantageously, the bearings 5 and 15 are not sub jected to loads acting in a different direction. Inside the el ement 14 is an electrical passageway element or rotatable elec tricity distributor 19 consisting of an inner part 192 and an outer part 194. The inner part 192 is anchored in the arm 42 with anchors 198 and the outer part rotates together with the casing 14 and thus with the axle 1.

Now, in the rotary device according to the invention, urea or an analogous additive is conducted via the aperture 20' in the element 2 to the conduit 20 (in the axle 1) along the inserted tube 201 through the casing 14 and the electricity distributor 19. It is also advantageous to conduct the electrical cable 202 in parallel with the urea tube 201. The consumption of applied urea per hour is only 30 1 ± 30 %. Based on its outer dimen sions, a ~ 10 mm ± 10 % flexible tube comprising a hole of approx. 5 mm ± 10 % can thus be used. The pressure can be 50 bar. It is further advantageous to make the conduit 20 in the axle 1 slightly askew (5° ± 20 %) with respect to the orienta tion of the axle 1. This way, it is easy to implement the pas sageways through the parts 14 and 19. It is also possible to make a separate conduit for the electrical cable, such as a conduit running from the aperture 20 via the conduit 20 in the axle 1 into the interior of the element 14. The diameter of the electrical cable is approx. 10 mm +30 %. The element 19 is technically known. In this respect, currently 2 passageways are required for a current of approx. 15A and 2 passageways are re quired for data transmission. The outer dimensions of such an electricity distributor 19 can be 85 mm ± 20 % and inside the hole can be 0 ~ 25 mm ± 20 %. In Figure 1, the electrical ca ble 202 running via the aperture 20 extends into the outer part of the element 19, said outer part rotating together with the axle 1. The inner part is rigid and the cable 2021 runs from here further to the control unit of the harvester head. The urea tube 201 comes out through the element 19 and the end of the tube 201 has a rotating connector 2011. The tube can be an chored, e.g., from the flange 141 of the element 14. However, the pressure in the connector 2011 only acts during

felling/sawing so that the rotary device does not work nor mally. When the rotating connector inside the tube is not sub jected to pressure, its moment of friction is very small and under 0,5 Nm ± 50 %.

The tubes from the rotating connector 2011 can continue side ways or in the direction of the tube. During maintenance or re pairs the tube 201 can be plugged at both ends. This way it is ensured that urea or an analogous substance does not intermix with the hydraulics. The tube 201 can be made of a rigid tube; however, in this case, its removal and installation first re quire the removal of the element 2. In this case, the outer di ameter of the tube can be 0 8 - 10 % and the conduit 20 is most preferably arranged dead centre .

The rotatable electrical connector, electricity distributor 19 is of a constant type, but must be co-axial, i.e. there is an opening running through its centre.

The processing fluid line hose, especially for urea, is advan tageously a conventional hydraulic hose. The latter thus has a pressure durability, but at the same time an abundant twisting strength for the rotatable connector. The hydraulic hose to the connector can be led from the aperture 20' downward through the conduit 20 in order to be connected to the rotatable connector 2011. The continuous hose is advantageously also a hydraulic hose and is fastened after a distance in the frame of the felling device, e.g. in its arm.

The rotating connector for the processing fluid line is advan tageously a rotatable hydraulic connector, e.g. TAIMI (USA) T2, ser . no. SZ90-F06M-F06F . The electricity distributor is, e.g., Rion TB 2586 P0410 S02 (RION ELECTRONIC CO., LIMITED, CN) .

Figures 3a to 3c show a felling device 45 according to a fur ther embodiment, which deviates only slightly from the preced ing design. The arm 42 comprises two flat shafts 42' between which are the attachment members 43 and 41 disclosed in Figure 2 and at the bottom of which is a rod 425 from which the actual frame of the felling head or harvester head is suspended. The rotary device and the rotatable distributors are integrated in the upper part of the arm, as in the embodiment shown in Figure 2. The hydraulic oil distributor 7, the gears and the rotary motor 13 are encased, inter alia, by means of the casing 421. The feed interfaces 132 of the motor 13 and the hydraulic in terfaces 211, 221, 231 are visible and available. The felling device 45 is supported here from the hanger 2 as well, more precisely from the pin 23 of the bracket 29, which supports the upper part of the universal joint 231 in a conven tional manner.

The arm 42 is also supported here by way of bearings from the axle 1, the upper part of which comprises the hanger 2. The central auxiliary fluid interface according to the invention exits from the rotatable connector 2010, more precisely from its lower part B.

From Figures 4A and 4b the rotating parts are clearly visible with respect to one another. Rigidly attached in the upper part of the axle 1 is the hanger 2 (Figure 4A) , which has articu lated means for its attachment to the boom. Here, the attach ment of the gear 3 to the hanger 2 with the flange 11 remaining between the two is realized as shown in the embodiment in Fig ure 2. Here, the hanger and axle have conduits 20, 21, 22, 23 while the hanger has corresponding apertures 20', 21', 22' and

23' for the leakage line. The hydraulic oil distributor 7 is of the same type as described above. Each conduit 21, 22, 23 is connected to its own groove on the surface of the axle 1, said grooves being commonly designated as the ring conduit system 171. The distributor 7 has corresponding ring conduits 172, which have couplings to the connectors 211, 221 and 231 in a manner known per se . Ring seals are disposed between the ring conduits in a known manner.

The bottom end of the axle 1 has a flange 10 made of the best material which interlocks with the extension 105 of the axle 1. The flange 10 and the gear 3 determine the axial position of the radial bearings 5 and the sleeve-like hydraulic oil dis tributor 7.

The version of the thrust bearing 15 shown in Figure 4a, i.e. its lower ring 151, is supported by means of the ring nut 16 arranged in the extension 105. This works as in the embodiment shown in Figure 2. The ring nut 16 supports the lower ring of the thrust bearing 15 and, by way of the balls, the upper ring 152. By means of the ring nut 16, the thrust bearing 15 is raised together with the support 41 (which is ring-shaped here) of the frame 4 to a height so that there remains a small clear ance between the gear 3 and the top of the upper end 43 of the frame 4.

The most essential difference here from the embodiment shown in Figure 2 is that the ring-shaped inner part 192 of the electri cal distributor 19 is fastened in the axle 1, more precisely in its lower end 14, and the ring-shaped outer part 192 is in the arm 42, more precisely in the flat shafts 42' on the bar 198. Attached to the lower end 14 is a conduit extension section 144, to the upper end of which the tube 201 is connected.

Connected to the lower end of the extension section 144 is a rotatable connector 2011, more precisely its upper end A, the lower end of the rotatable connector 2011 being joined by a mo ment connection to the lower end of the casing 196. The rotat ing lower part B exits the casing 196 and an extension tube 2013 is connected to it in order to deliver processing fluid to the nozzles. The moment generated by the tube for urea, etc. is also sufficient here in order to cause the lower part B to ro tate vis-a-vis the upper part A.

The central line can also be utilized for oil delivery by means of its high pressures if a processing fluid line is not re quired. Such an alternative would be, e.g., a straight line leading to a hydraulic accumulator.

Figures 5a and 5b show two sections of a new embodiment, one through the motor and the other perpendicular thereto so that the different conduits 20, 21 are visible. In Figure 5a a hy draulic oil conduit 22 inside the axle is visible. In Figure 5b, the same conduit 20 as shown in Figure 4a is visible. Fig ure 5b shows the arrangement of the motor 13 in the frame 4 and a driver gear 33 connected to its axle. The latter is supported from the frame 4 with needle bearings 331.

List of parts

1 main axle with its conduits 13 motor

10 support sleeve 132 motor feed

105 axle extension 14 lower end

106 extension (Fig. 2) 144 intermediate tube

11 flange 145 lower casing (Fig. 5)

2 hanger 5 radial bearing

20 additional conduit 51 inner ring of bearing ( aperture 20')

52 outer ring of bearing

201 additive fluid tube

15 thrust bearing

2011 rotating connector

151 lower ring of bearing

A inner part, B outer part

152 upper ring of bearing 2013 hose connector

16 ring nut

202 electrical cable

19 co-axial electrical con

21 hydraulic oil conduit nector

21 aperture 192 inner part

22 hydraulic oil conduit 194 rotating outer part 22 ' aperture 196 lower casing

28 leakage line, aperture 28' 198 moment support

29 bracket 30 harvester head

23 hanger pin 18 bolts

231 upper joint 35 felling head, e.g. har vester head

3 gear

36 feeding device

33 driver gear

38 cutting saw

331 needle bearings

39 tree to be processed

4 outer ring

37 base machine

42 arm

371 caterpillar track

42 side shaft of arm

50 boom/arms

45 entire felling device

52 lifting arm

6, 12 glide rings

53 folding arm

7 distributor (hydraulic oil)

57 adapter

71 seals

171 inner ring conduits

172 outer ring conduits