FI127585B - Wood grab arm - Google Patents

Abstract

The invention relates to a hydraulic actuator (10) comprising two or more interconnected cylinder parts (11, 12), namely an outer cylinder part (11) and an inner cylinder part (12), each cylinder parts comprising a piston (13.1, 13.2). ) and a piston rod (14.1, 14.2) adapted to form the actuator (15, 16) and a roller part (17.1, 17.2) into which the actuator is fitted; chamber compartments (A, B) adapted to be formed for each cylinder portion and a pressure medium feeder arrangement (25, 26) to generate the actuator's movement (M1, M2) with the pressure medium directed to the chamber compartments. A separate feeder arrangement for pressure medium has been adapted for the chamber spaces of the cylinder parts. In addition, the invention relates to a system for controlling the function of the hydraulic actuator (10) and an energy digger (40).

Description

(54) Name of the invention - Uppfinningens benämning

energy wood

Energivedgripare (56) References - Anförda publikationer

DE 19747298 A1, FR 999277 A, DE 3339851 C1 (57) Abstract - Sammandrag

The invention relates to a hydraulic actuator (10) comprising two or more cylindrical parts (11, 12) arranged in relation to one another, namely an outer cylinder part (11) and an inner cylinder part (12), each cylinder part comprising a piston (13.1, 13.2) and a piston rod 14.1, 14.2) arranged to form an actuator (15, 16) and a cylindrical part (17.1, 17.2) into which the actuator is arranged; chamber spaces (A, B) adapted to form each cylinder member and a pressure medium supply arrangement (25, 26) for effecting the actuator movement (M1, M2) by the pressure medium introduced into the chamber spaces. The chamber sections of the cylinder sections are provided with their own pressure medium supply arrangements. Further, the invention also relates to a system for controlling the operation of the hydraulic actuator (10) and an energy wood grapple (40).

Uppfinningen avser et hydrauliskt maneuver (10), som innefattar eller flera in i varandra inpassade cylinderdelar (11, 12), nämligen en yttre cylinderdel (11) och en inre cylinderdel (12), hoisted roddelar innefattar en kolv (13.1, 13.2) ) och en kolvstang (14.1, 14.2) anpassade för att bilda maneuvering (15, 16) och en valsdel (17.1, 17.2), i maneuvering the inpassats; chamber trimming (A, B) anpassade att image for a respiratory cylinderdel and a matararrangemang (25, 26) for tryckmedium for att generating maneuvers (M1, M2) med tryckmediet som lefts till chamber trem. Ett skilt matararrangemang för tryckmedium har anpassats för cylinderdelarnas chamber drum. Dessutom avser uppfinningen et system för att styra det hydrauliska maneuvering (10) function och en energivedgripare (40).

energygrapples

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The invention relates to an energy wood grapple comprising:

- body,

- a trimming machine fitted to the trunk,

- a hydraulic actuator adapted to actuate a cut-off device comprising a hydraulic actuator

- two or more cylindrical parts arranged relative to one another, namely an inner cylinder part and an outer cylinder part, each cylinder part comprising a piston and a piston rod arranged to form an actuator and a cylindrical part into which the actuator is inserted and the inner piston part of Whereas the piston arms of the institutions are partly fitted outside the actuator;

- chamber spaces adapted to form each cylinder member,

- a pressure medium supply arrangement for effecting movement of the actuator by means of pressure medium introduced into the chamber chamber 25,

- control means for controlling the operation of the hydraulic actuator.

For example, excavators have been manufactured with energy tree grabs, which allow standing trees to be felled and moved to a desired location after felling. At its simplest, a sharpened counter blade is added to the log grapple. When closing the clamp or the like, the wood is pressed against the counter blade while cutting off.

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After cutting, the wood is under the control of a clamp and can be moved to the desired location. An energy tree grapple can also take several trees at a time.

Energy wood grabs can be used on other machines than just the aforementioned excavators. Regardless of the machine being used, changing and working smoothly is the most important factor when it comes to working with machines.

Nowadays more and more the excavator is equipped with a bucket rotor. It poses challenges in clearing with an energy wood grapple as the pressure on the rotor is reduced to about 220 bar. At the same time, the oil flow is also throttling as it passes through the rotor. Thus, a larger cylinder is needed for cutting large wood, which, for the reasons mentioned above, again has a relatively low speed of movement and slows down the grapple. This significantly affects machine productivity. In the prior art, the cutting device uses a cylinder having a piston of 110 mm and requiring a pressure of 280 to 300 bar. In this case the lower pressure of 220 bar due to the rotator is not sufficient for the cylinder. The same problems of cylinder speed and power exist in other industries as well, not just in the energy harvesting example mentioned.

The object of the invention is to provide a functionally improved energy wood grapple. The features of the invention are set forth in claim 1.

With the nested cylinder structure, the hydraulic actuator can first perform rapid movement with the actuator of the smaller cylinder part and only when necessary, utilize the maximum power produced by the actuator of the larger cylinder part.

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In an exemplary embodiment of the energy log grapple embodiment, when working with a small wood, only the piston of the inner cylinder part, which is smaller than the piston of the outer cylinder part, moves in the hydraulic actuator and is thus quick to work. When a larger tree is encountered and the inner or smaller cylinder of the hydraulic actuator no longer has sufficient force, then the larger piston of its outer cylinder part becomes involved. The hydraulic actuator can be controlled automatically. With the invention, the power of the hydraulic actuator 10 is sufficient in an energy log grapple to cut even heavy trees, but its operation is still rapid. Another embodiment of the invention may also be valve machines. They may have the same operating principle as an energy grapple. In this case, instead of cutting the tree, it is only a log splitting.

However, the benefits are largely the same.

The invention has several different embodiments. In one embodiment, the pressurized medium that causes the lower or inner cylinder to move can be introduced into the hydraulic actuator through its piston rod and lead to a chamber space limited by the smaller or inner cylinder member piston and the larger cylinder member piston and piston rod. This causes movement of the smaller cylinder part.

In another embodiment, the pressure medium that causes the movement of the smaller cylinder to be actuated can be introduced into the hydraulic actuator through the piston of the larger, i.e., outer, and smaller, or inner, cylindrical portions and lead to the chamber space defined by the smaller or inner cylindrical piston. Hereby, part of the chamber space of the smaller cylinder part may also be formed inside the piston rod of the inner cylinder part. This embodiment provides the working motion of the inner cylinder member by applying pressure medium to the piston of the inner cylinder member on both sides thereof.

Further, in this embodiment, all pressure medium connections are provided at one end of the hydraulic actuator, which is preferably stationary. In this case, they and their associated pressure media-

5 Kuts are protected and in addition is minimal. to them on business stress With hydraulic actuator can be solve for example

20165753 prh 16 -08-2017 challenges of low oil production and reduced pressure. Other additional advantages achieved by the invention will be apparent from the description and features of the appended claims.

The invention, which is not limited to the following embodiments and embodiments, will be further described with reference to the accompanying drawings, in which:

Figures 1-5 show conceptual examples of a hydraulic actuator in longitudinal section and

Fig. 6 shows a basic example of an energy wood grapple having a cutting actuator equipped with a hydraulic actuator according to one of Figs.

Figures 1-5 show, in principle, some embodiments of the hydraulic actuators 10 in cross-sectional view, which implement the principle inherent in the invention. Instead of a hydraulic actuator, it is also possible to speak of a hydraulic cylinder in a more popular language. The hydraulic actuator 10 comprises two or more cylinder parts in its basic form

11, 12, chamber chambers A, B adapted to form for each cylinder part 11, 12 a hydraulic actuator 10 and a pressure medium supply arrangement 25, 26 connected to chamber chambers A,

B.

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The hydraulic actuator 10 comprises two or more cylinder parts 11, 12 which are nested within one another.

In the embodiments shown, there are two cylinder parts 11, 12.

Hereby, the cylinder parts 11, 12 can be said to be coaxially actuated in the actuator, but also telescopically. For example, the cylinder members may be referred to as the outer cylinder member 11 and the inner cylinder member 12. In this case, the inner cylinder member 12 is partially inside the outer cylinder member 11, i.e. also closer to the central axis of the actuator. In contrast to Salo no, the outer cylinder part 11 is then around the inner cylinder part 12. Thus, the inner cylinder part 12 is also smaller than the cylinder parts and the outer cylinder part 11 larger.

Each cylinder member 11, 12 has a piston 13.1, 13.2 and a piston rod 14.1, 14.2 connected at one end to a piston 13.1, 13.2 known per se. Together, the piston 13.1, 13.2 and the piston rod 14.1, 14.2 form an actuator 15, 16. In addition, each cylinder part 11, 12 also comprises, in a manner known per se, a cylindrical part 17.1, 17.2. The actuator 15, 16 or at least its piston 13.1, 13.2 is disposed within the cylindrical part 17.1, 17.2. The cylindrical part 17.1 of the outer cylinder part 11 now functions as the outer jacket of the hydraulic actuator 10. The hollow piston rod 14.1 of the outer cylinder part 11 now acts as a cylindrical part 17.2 of the inner cylinder part 12.

For example, the hydraulic actuator 10 may have attachment stops 33.1, 33.2 at both ends to provide actuator actuation. Now the fastening stops 33.1, 33.2 are loops. Thereby, a cylindrical portion 17.1 has a loop 33.1 at its end and an opposite loop 33.2 at the opposite end of the actuator 10 at the end of the piston rod 14.2 of the inner cylinder portion 12. Typically, the hydraulic actuator 10 is adapted to its application such that the cylindrical part 17.1 of the outer cylinder part 11, i.e. its casing, is at a suitable position, such as, for example, just a loop

33.1, closed at the application site and actuators 15, 16 move relative to the cylindrical parts 17.1, 17.2. Of course, this can be the other way round, depending of course on the application. Alternatively, both parts of the application move as a result of the use of the hydraulic actuator 10, for example if they are articulated to one another.

Each cylinder part 11, 12 is arranged to form chamber spaces A, B in the actuator to effect at least movement M1, M2. The chamber space A, B is delimited by actuator structures such as actuators 15, 16 and more particularly by piston rod 13.1, 13.2, piston rod 14.1, 14.2 and inner surfaces of cylindrical section 17.1, 17.2. The volume of chamber spaces A, B may change. The chamber space B can also be very small, such as in the situation where the pistons 13.1, 13.2 are completely closed, but can be said to be formed when a pressure medium is moved between the pistons 13.1, 13.2 which moves at least one actuator 16.

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The hydraulic actuator 10 also includes a pressure medium supply arrangement 25, 26 for effecting the working movement M1, M2 of the actuator 15, 16 by the pressure medium introduced into the chamber spaces A, B. The pressure medium supply arrangement 25, 26 may include, for example, ducts, connections 18.1 to 18.7, valves 39, and control means 20 which, for example, control the flow of pressure medium between the various connections and ducts, e.g. The pressure medium is typically, for example, hydraulic oil.

The chamber compartments A, B of the cylinder parts 11, 12 are provided with their own pressure medium supply arrangements 25, 26. Thus, the chamber B of the inner cylinder part 12 is provided with its own independent or separately arranged pressure medium supply. Thus, each cylinder part 11, 12 can be used as its own unit 35 individually or, if necessary, together.

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Due to the nested nature of the cylinder parts 11, 12, they have different pressure areas. The piston 13.2 of the inner cylinder part 12 is then smaller and the piston 13.1 of the outer cylinder part 11 larger. Thus, at the same flow rate, the smaller or inner cylinder member 12 moves faster than the larger, i.e. outer cylinder member 11. Independent pressurized fluid feeds to both cylinder members 11, 12 and thus actuation of the actuators 15, 16 provide, for example, an operating speed advantage.

In addition, the chamber spaces A, B of the cylinder members 11, 12 may be disconnected or at least without a substantial pressure-medium connection between the chamber spaces A, B. When the chamber space B of the inner cylinder part 12 and the chamber space A of the outer cylinder part 11 are disconnected, the supply of pressure intermediate to one chamber space B does not substantially affect the second chamber space A and thus the cylinder part 11 provided thereon.

In each of the embodiments shown in Figures 1-5, the pressure medium supply arrangement 26 of the inner cylinder member 12, which now includes fittings and flow channels, is disposed at least partially within the piston rod 14.2 of the inner cylinder member 12. To this end, at least a passage for a pressure medium is provided inside the piston rod 14.2. Further, in the embodiment shown in Figures 2-5, the chamber space B of the inner cylinder member 12 is arranged to form at least partially a hollow piston rod of the inner cylinder member 12.

14.2 inside.

In the embodiment of Figure 1, the chamber space B, in turn, is outside the piston rod 14.2 of the inner cylinder part 12. Then, chamber space B is arranged to form between the piston 13.2 of the inner cylinder part 12 and the piston 13.1 of the outer cylinder part 11, and

20165753 prh 16 -08-2017 thus a cylindrical space inside the hollow piston rod 14.1 delimited by the outer cylinder part 11. Herein, the pressure medium supply arrangement 26 to the chamber space B of the inner cylinder part 12 is implemented by a channel 34 formed in the piston rod 14.2 of the inner cylinder member 12 and passing through the piston rod 14.2 with a connector 18.7.

In the embodiment of Figure 4, the chamber space B, in turn, is partially inside the hollow piston rod 14.2 of the inner cylinder part 12 and also outside it between the pistons 13.1, 13.2. Thereby, part of the chamber space B is arranged to be formed between the piston 13.2 of the inner cylinder part 12 and the piston 13.1 of the outer cylinder part 11, and thus the cylindrical space inside the hollow piston rod 14.1 bounded by the piston rod 14.1. In addition to Li15, part of the chamber space B is also arranged to form inside the hollow piston rod 14.2 of the inner cylinder part 12. Here, the pressure medium supply arrangement 26 to the chamber space B of the inner cylinder part 12 is provided by a passageway 36 inserted through the piston 13.1 of the outer cylinder part 11 and connected to the connector 18.6, the embodiment of which will be described in more detail below in another embodiment.

Further, the chamber space B of the inner cylinder part 12 can be said to be arranged in each embodiment to form on the piston rod side 14.1 of the outer cylinder part 11. Further, the chamber space B of the inner cylinder part 12 can then be said to be adapted to form inside the hollow piston rod 14.1 of the outer cylinder part 11 for at least part of its working length. Hereby, the chamber space B may be directly limited to the hollow piston rod 14.1 of the outer cylinder part or may be inside the hollow piston rod 14.2 of the inner cylinder part, which in turn is also on the piston rod 14.1 of the outer cylinder part 11.

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Figures 2, 3 and 5, in turn, show an embodiment in which chamber space B of the inner cylinder part 12 is divided into two sub-chambers BI, B2. Of these, the first sub-chamber B1 is within the hollow piston rod 14.2 of the inner cylinder member 12. The second sub-chamber B2 is in turn located on the piston rod of the inner cylinder part 12

14.2 on the opposite side of the piston 13.2. Thus, it is possible for the inner cylinder part 12 to be subjected to a working movement M1 by a pressurized medium applied to both sides of its piston 13.2 and thereby ensure its operation in all paths of space. In other words, this gives more pressure surface.

Figures 2, 3 and 5 also show an embodiment in which chamber space B is divided into two sub-chambers BI, B2 by a distribution structure 22. Now, the pressure medium 26 of the inner cylinder member 12 includes a hollow piston rod of the inner cylinder member 12.

14.2 A dividing structure 22 disposed within the formed chamber 22. With the dividing structure 22, the piston rod 14.2 of the inner cylinder part 12 is divided into two chamber parts B1, D1. One of the chamber portions B1 is adapted to form part of chamber space B, i.e. to form at least partially a chamber space B which causes the inner cylinder part 12 to move by the movement M2, with a divider structure 22 dividing the hollow piston rod 14.2 into simple pressure medium ducting.

Further, Figures 2, 3 and 5 also show an example for implementing the distribution structure 22 in more detail. Now, the divider structure 22 includes a static divider member 23 and a bracket 24 arranged on it. The divider member 23 is an inner cylinder member

12 inside the hollow piston rod 14.2. It is tight on the piston rod

14.2, for example, against a cylindrical inner surface and may have seals (not shown) on the outer periphery thereof. It is thus a kind of stationary piston within the hollow piston rod 14.2 of the inner cylinder part 12. Hereby, the inner cylinder part 12 can be said to have two pistons; a piston 13.2 at the end of the piston rod 14.2 and a second piston formed by a dividing structure 23 inside the piston rod 14.2. The chamber part B1, which is part of the chamber space B, is then located on the dispensing member 23, on the piston rod.

14.2 in a space delimited by the inner surface and the end of the piston rod 14.2, the end being opposite to the piston 13.2 of the inner cylinder part 12. Correspondingly, the chamber portion D1 is in a space defined by the manifold 23, the inner surface of the piston rod 14.2 and the piston 13.2 on the opposite side of the manifold 23 relative to the chamber portion B1. The actuator 16 of the inner cylinder part 12, and more particularly in this case the piston rod 14.2, is arranged to move with respect to the dispensing member 23.

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The dividing structure 22 further includes a support 24 for the distribution member 23 guided through the pistons 13.1, 13.2 of the cylindrical parts 11, 12 through the hollow piston rod 14.2 of the inner cylinder part. The bracket 24 is now formed by an elongate member, a shaft 37, disposed in the longitudinal direction of the hydraulic actuator 10 on its central axis. Here, the bracket 24 may rest at one end on the end wall of the cylindrical portion 17.1 of the hydraulic actuator 10, pass through chamber A of the outer cylinder portion 11 and further through the piston 13.1 of the outer cylinder portion 11, through the sub

12 inside the hollow piston rod 14.2. There it passes through the chamber portion

D1 through to the dispenser 23 attached thereto. Thus, it can hold the divider 23 in place within the hollow piston rod 14.2 of the inner cylinder member 12. The pistons 13.1, 13.2 have openings and seals for the passage of the arm 37. This allows movement of the pistons 13.1, 13.2 around the stationary shaft 37. The pipe 35 of the embodiment of Figure 4 may be implemented with the same operating principle.

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By means of the bracket 24 and guided through the divider 23, a pressure medium supply arrangement 26 may be provided for the chamber space B of the inner cylinder part 12. 16, at least in the working direction M2, or alternatively even in both directions, as is the case in the embodiments of Figures 2, 3 and 5. The passageways 27, 28 include an inner passageway 27 disposed on the arm 37 and connected to the connector 18.4, adapted to pass through the dispensing member 23 to introduce pressure medium into chamber space B and now more particularly B1 and thereby effect a working movement M2. In addition, the passages also include an outer passage 28 disposed on the arm 37 and connected to the connector 18.5 and adapted to conduct pressure medium on the opposite side of the dispensing member 13 to the chamber space B1, now to the chamber space D1. This causes a return movement, i.e. movement in the opposite direction to the work movement M2, to the inner cylinder part 12.

Figures 2, 3 and 5 also show an embodiment in which the inner cylinder part 12 is provided with a bore 30 in the hollow tube casing 29.2 formed by the piston rod 14.2 and also in the piston 13.2 to guide the pressure medium from the first sub-chamber B1 to the second sub-chamber B2 to effect the movement M2. This provides a simple way of delivering the pressure medium also outside the actuator 16, whereby it can also be subjected to an actuating force on one side of the piston 13.2 relative to the chamber portion B1, thereby securing motion of the actuator 16 without The piston rod 14.2 of the hollow shell 29 of the working pressure of the medium exports to simplify the implementation of the hydraulic actuator 10 in the interior.

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Figure 3 shows an embodiment in which the piston rod 14.2 of the inner cylinder member 12 is provided with a channeling 31 for guiding the pressure medium into the piston rod of the inner cylinder member 12.

14.2 and a space 32 between the piston rod 14.1 of the outer cylinder member 11 to effect a negative movement of the actuators 15, 16. Thus, in this embodiment, the pressure medium applied to the chamber portion D1 through the channel 28 fitted to the bracket 24 is further directed through the channel 31 to the chamber 32. This ensures the recovery of the inner and outer cylinder parts 12, 11 after the movement. In other words, this also provides more pressure surface for recovery.

The pressure medium supply arrangements 25, 26 may include the ports, as well as the aforementioned common associated channels, for delivering the agent 15 to the desired chambers. The working motion M1 of the outermost cylinder part 11 is achieved by the pressure medium supplied to the first chamber A, opposite to the piston rod 14.1, i.e. the outermost cylindrical part 17.1. The assembly 18.1 and the associated conduit 38, more generally, first means for introducing the pressure medium into a chamber space A formed on the outer cylinder part 11, the hydraulic actuator 10 also include other means for guiding the pressure medium to the outer cylinder part 11 for actuating the actuator 16 of the cylinder member 12 independently of the actuator 15 of the outer cylinder member 11. The second chamber space B, which can be formed on the inner cylinder part 12, is arranged on the piston rod of the outer cylinder part 11.

14.1 inside at least part of the working length. At the same time, the second chamber space B is on the opposite side of the piston 13.1 of the outer cylinder part 11 with respect to the first chamber space A.

20165753 prh 16 -08- 2017 ίο

As already seen in the embodiments of Figures 1-5, the hydraulic actuator 10 may be twofold. In the embodiments of Figures 1 and 3, the return movement of the outer cylinder member 11 is further provided by the common pressurized fluid 18.2, 18.3 which acts on the outer cylinder member 11 on the piston 13.1 from its piston rod side 14.1. In Figure 1, the return movement of the inner cylinder member 12 is further provided by a pressure medium applied to the connector 18.3 which acts on the piston 13.2 of the inner cylinder member 12 from the side of its piston rod 14.2.

In addition to the hydraulic actuator 10, the invention also relates to a system for controlling the operation of the hydraulic actuator 10. The system comprises one or more hydraulic actuators 10 and control means 20 for controlling the operation of the hydraulic actuator 10. The hydraulic actuator 10 comprises two or more mutually fitted cylinder members 11, 12, namely an inner cylinder member 12 and an outer cylinder member 11, each of which includes a piston 13.1, 13.2 and a piston rod 14.1, 14.2 arranged to form an actuator 15, , 17.2 into which the actuator 15, 16 is disposed. In addition, the actuator also includes chamber spaces A, B arranged to form each cylinder member 11, 12, and a pressure medium supply arrangement 25, 26 to effect actuator movement M1, M2 of the actuator 15, 16 by pressure medium introduced into chamber spaces A, B. The control means 20 are arranged to control the operation of the hydraulic actuator 10.

In one or more hydraulic actuators 30 of the system, the chamber spaces A, B of the cylinder parts 11, 12 are provided with their own pressure medium supply arrangements 25, 26. Examples thereof are shown in Figures 1-5. The control means 20 are adapted to control the pressure medium supply arrangement 25, 26 in order to effect the movement M2, M1 progressively first by the inner cylinder part 12, more specifically by its actuator 16, and subsequently by the outer cylinder part 11, more specifically by its actuator 10. is particularly advantageous, for example, in lower pressure and lower volume flow applications, such as when using an energy harvester grapple with a rotator.

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Fig. 6 shows an embodiment of the use of the hydraulic actuator 10. Fig. 6 shows an exemplary energy10 wood grapple 40 in which a hydraulic actuator can be utilized

10. The energy wood grapple 40 includes a frame 52, a cutting device 41 for cutting wood and a hydraulic actuator 10 adapted to drive the cutting device 41. The hydraulic actuator is now, for example, one of the hydraulic actuators 10 shown above. cylinder members 11, 12, namely an inner cylinder member 12 and an outer cylinder member 11, each cylinder member 11, 12 comprising a piston 13.1, 13.2 and a piston rod 14.1, 14.2 arranged to form an actuator 15, 16 and a cylindrical member 17.1, 17.2 into which fitted. In addition, the hydraulic actuator 10 also includes chamber spaces A, B arranged to form each cylinder member 11, 12. In addition, the energy wood grapple 40 includes control means 20 for controlling the operation of the hydraulic actuator 10.

In the hydraulic actuator 10, the chamber spaces A, B of the cylinder parts 11, 12 are fitted with their own pressure medium supply arrangements 25, 26. The control means 20 are arranged to control the pressure medium supply arrangement 25, 26 in step with the inner cylinder member 12 and The criterion may be, for example, a pressure criterion for which a limit value is set. When this is exceeded, the pressure medium is supplied to the outer cylinder part 11 and thus more force is obtained on the cutting.

The cutting device 41 may be, for example, a functional assembly formed by the clamp 50 shown in the figure and the cutting blade 51. In this case, the hydraulic actuator 10 is adapted to act, for example, on the forceps 50. The cutting device 41 may also be based, for example, on a guillotine cut. As such, its blade moves and the hydraulic actuator 10 acts on its blade. The energy wood grapple 40 may also have pruning means, such as a pruning blade (not shown).

In the embodiment of Figure 6, this is a single-action grapple in which, with one clamp 50, the wood is pressed against the blade 51. The clamp 50 defines the body 52 with the friction 53. The wood presses against the oblique blade 51 while cutting off. At the narrow end of the body 52, the energy wood grapple 40 is rigidly secured to, for example, the boom of an excavator. In between, there may be a rotator or rotator of an energy wood grapple 40.

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The single-lever grapple clamp 50 may be operated by a single hydraulic actuator 10 disposed within the housing-like body 52. In this case, the hydraulic actuator 10 is secured to, for example, the body 52 of the energy wood grapple 40 by its loop 33.1 at the end of the cylindrical portion 17.1. Thus, the actuator 10 is well protected. At the same time, a short but large cylinder can be used. With the hydraulic actuator 10, the movement of the clamp 50 is quick and, at the same time, efficient for cutting thick wood.

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Next, the operation of the energy wood grapple 40 and also the hydraulic actuator 10 shown in Figs. When the clamps 50 are open, the actuators 15, 16 of the actuator 10 are within the cylindrical parts 17.1, 17.2 such that the actuator 10 is in its shortest position. Their pistons 13.1, 13.2 can then be engaged with one another and at the end 33.3 of the loop portion 17.1 of the cylindrical part 17.1. When the energy wood grapple 40 is introduced to the wood, the clamp 50 is closed. The pressure medium is then passed through the common actuator 18.4, 18.6 and 18.7 and the associated passageway 27, 34, 36 to chamber B, (B1 and B2). As a result, the actuator 16 of the inner cylinder part 12 starts to project outwardly, i.e. its movement M2 is obtained. In this case, for example, the pressure-controlled sequence valve 39 shown in Figure 5 prevents the flow of pressure medium 15 from entering the channel 38 now closed only by the plug 19 and thus into the chamber A of the outer cylinder part 11. Of course, other ways of controlling pressure media supply are possible. Integrated with the sequence valve 39 in the hydraulic actuator 10, one single and associated fluid tubing can be avoided.

If the wood is cut by the movement M2 of only the inner cylinder part 12, the movement M1 of the outer cylinder part 11 is not needed at all. The kat25 generated by the inner cylinder member 12 alone is relatively rapid per event compared to, for example, cutting the wood with a conventional telescopic cylinder where work is commenced at the outermost or larger cylinder member and the smaller inner cylinder members only enter the outermost and largest cylinder member.

However, if the wood is not cut by the motion M1 of the inner cylinder alone, then its motion will either be slowed down or even stopped. As a result, the pressure rises to the first cause17

20165753 prh 16 -08-2017 cylinder member 12 chamber spaces B pressure medium in a conductive line, more generally in a pressure circuit. Thus, for example, the pressure-controlled sequence valve 39 shown in FIG. It causes motion M1 of the actuator 15 of the outer cylinder part 11. In the chamber space B of the inner cylinder part 12, the pressure medium previously introduced is either retained or discharged there, depending on the implementation. In this case, the piston 13.1 of the actuator 15 of the outer cylinder part 11 either pushes the piston 13.2 of the inner cylinder part 12 through the pressure medium of the chamber B or reaches the piston 13.2 and thereby further moves the actuator 16 of the inner cylinder part. which will definitely cut the tree.

The available stroke length and / or force for the entire hydraulic actuator 10 may not be required for cutting. This can be taken into account when installing the hydraulic actuator 10 in the energy log grapple 40. In addition, the stroke lengths of the actuators 15, 16 of the cylinder members 11, 12, for example, can be limited. If, for example, maximum force is not needed throughout the range of motion, then the movement of the piston 13.1 of the outer or larger cylinder part may be limited to a shorter distance.

In the embodiments of Figures 2, 3 and 5, it is also possible to set the extreme length of the hydraulic actuator 10. Here, the arm 37 constituting the support 24 of the divider 22 and the divider 23 disposed at its end can be utilized to limit the extreme length of the hydraulic actuator 10 to the desired length. This can be determined by the length of the arm 37 and thus the location of the distributor member 23 within the piston rod 14.2 of the inner cylinder part 12. Outer, or bigger

20165753 prh 16 -08-2017 the maximum force produced by the cylinder member 11 is only available at its structural stroke length. In this case, the cylinder will no longer produce the same amount of force (unless the emptying of the inner or smaller cylinder 12 is prevented). Further, the embodiments of Figures 2, 3 and 5 are also advantageous in that all of the connections are in the cylindrical part 17.1 of the hydraulic actuator 10, which is generally subject to little, if any, movement. Thereby, the associated hoses are subject to little movement stress and, moreover, are protected, for example, within the body 52 of the application device.

Similarly, the opening of the clamp 50 is accomplished by the reverse or negative movement of the hydraulic actuator. In this case, the pressure medium is discharged from chambers B and A and common respectively

18.2, 18.3 and 18.5, the pressure medium is further passed through the channels to the chambers connected thereto. In this case, both actuators 15, 16 can be actuated to ensure a safe opening of the clamp even if, for example, the truncated wood is wedged in the cutting device 41.

Pilot tests conducted by the applicant with an energy log grapple have found that in the energy log harvesting, the inner, or smaller, cylinder part 12 can cut up to 80% of the tree at certain types of work sites (eg field trenches).

The invention thus significantly speeds up the harvesting operation and thus increases its productivity.

With the hydraulic actuator 10 according to the invention and the system comprising such, the lower or lower cylinder part 12 and more particularly its actuator 16 achieve greater movement speed with less load and only when necessary a larger surface area, i.e. an outer and thus larger cylinder part 15 for greater force. The si35 part of the cylinder parts can also be referred to as the telescopic part.

One skilled in the art will recognize that there are several other ways of controlling the movements of the cylinder members 11, 12 and the actions obtained therefrom, including stepwise operation of the cylinder members 11, 12, for control means 20 (valves). As shown in Figure 5, the sequence valve 39 may be internal, that is, integrated with or within the actuator 10, or may also be external. When the sequence valve 39 is in use, the control means 20 may comprise only a conventional directional valve brick. One way is to apply one or more pressure transmitters somewhere in the circuit and on / off valves. Further, one skilled in the art will recognize that when pressure medium is introduced into one chamber, then pressure medium is removed from its counter chamber. In addition, the pressure areas of the pistons 13.1, 13.2 can be adapted to achieve an optimum force / motion ratio for each application. As an example of piston 13.1,

13.2 The diameters can be 130 mm and 80 mm.

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Claims (10)

1. Energy diggers, which include - a body (52), - a cutting device (41) arranged in the frame (52) for cutting the tree, - a hydraulic actuator (10) arranged to drive the cutting device (41), comprising hydraulic actuator (10) - two or more cylindrical parts (11, 12) which are fitted together, namely an inner cylinder part (12) and an outer cylinder part (11), each cylinder parts (11, 12) comprising a piston (13.1, 13.2) and a piston rod (14.1 , 14.2) adapted to form the actuator (15, 16) and a roller part (17.1, 17.2) into which the actuator (15, 16) is fitted, and the piston (13.2) of the inner cylinder part 12 is arranged inside the outer cylinder part (11) piston rods (14.1), and which piston rods (14.1, 14.2) of the actuators (15, 16) are arranged partially outside the actuator (10), - chamber spaces (A, B) adapted to be formed for respective cylinder parts (11, 12), a pressure medium feeder arrangement (25, 26) for generating the operating motion (M1, M2) of the actuator (15, 16) with the pressure medium delivered to the chamber spaces (A, B), control means (20) for controlling the function of the hydraulic actuator (10), characterized in that - a separate feeding arrangement (25, 26) for pressure medium is arranged in the hydraulic actuator (10) for the chamber spaces (A, B) of the cylinder parts (11, 12). 20165753 prh 15 -05- 2018 - the control means (20) are arranged to control the pressure medium feeder arrangement (25, 26) to generate a working movement (M2, M1) stepwise first with the inner cylinder part (12) and then, when the set pressure criterion is met, with the outer cylinder part ( 11). Energy gripper according to claim 1, characterized in that the pressure medium feeding arrangement (26) of the inner cylinder part (12) of the actuator (10) is arranged inside the piston rod (14.2) of the inner cylinder part (12). Energy gripper according to claim 1 or 2, characterized in that the chamber space (B) of the inner cylinder part (12) of the actuator (10) is arranged to be formed at least partially within the piston rod (14.2) of the inner cylinder part (12). Energy digger according to any of claims 1-3, characterized in that the chamber space (B) of the inner cylinder part (12) of the actuator (10) is divided into two sub-chambers (BI, B2), of which the first sub-chamber (BI) is inside the the piston rod (14.2) of the inner cylinder part (12) and the second sub-chamber (B2) are in relation to the piston rod (14.2) of the inner cylinder part (12) on the opposite side of the piston (13.2). Energy gripper according to any of claims 1-4, characterized in that the pressure medium feeding arrangement (26) of the inner cylinder part (12) of the actuator (10) comprises a dividing structure (22) arranged in the chamber formed inside the piston rods (14.2 of the inner cylinder part) (12). ) to divide the piston rod (14.2) of the inner cylinder part (12) into two chamber parts (BI, DI), one of which is arranged to be included in the chamber space (B) of the inner cylinder part (12). Energy digger according to claim 5, characterized in that the partition structure (22) comprises 20165753 prh 15 -05- 2018 - a dividing member (23) relative to which the actuator (16) of the inner cylinder part (12) is arranged to move, - a piston (13.1, through the pistons of the cylinder parts (11, 12), 13.2) guided into the piston rod (14.2) of the inner cylinder part (12) led support system (24) for the dividing means (23), - coaxially arranged channels (27, 28) for the pressure medium for the support system (24) for moving the actuator (16) of the inner cylinder part (12), which channels (27, 28) comprise an inner channel (27) arranged through the dividing means (23). ) for conveying pressure medium to the chamber space (B) and an outer channel (28) arranged to direct pressure medium to the opposing side of the dividing member (13) relative to the chamber space (B). Energy gripper according to any one of claims 4-6, characterized in that in the inner cylinder part (12) of the piston closure (14) and piston (13) of the actuator (10) a casing (30) is arranged to direct pressure medium to the the second sub-chamber (B2). An energy gripper according to any one of claims 1-7, characterized in that a piston (31) is arranged in the inner cylinder part (12) of the actuator part (12) and / or piston rod (14.2) for passing pressure medium to a space ( 32) between the piston rod (14.2) of the inner cylinder part (12) and the piston rod (14.1) of the outer cylinder part (11) to generate the negative movement of the actuator (15, 16). An energy digger according to claim 1 or 2, characterized in that the actuator (10) - the chamber space (B) of the inner cylinder part (12) is arranged to be formed between the piston (13.2) of the inner cylinder part (12) and the piston (13.1) of the outer cylinder part (11), - pressure medium feeder arrangement (26) for the chamber space (B) of the inner cylinder part (12) is arranged via the piston rod (14.2) and piston (13.2) of the inner cylinder part (12). 10. An energy gripper according to any one of claims 5-9, characterized in that with the dividing structure (22), the maximum length of the hydraulic actuator (10) is adjusted. 20165753 prh 15 -05- 2018 20165753 prh 06 -10- 2016 CM CO co