FI129652B

FI129652B - Hydraulinen järjestelmä sahalaitteiston ohjaamiseksi

Info

Publication number: FI129652B
Application number: FI20195915A
Authority: FI
Inventors: Toni Jormanainen; Arto Alfthan
Original assignee: Waratah Om Oy
Priority date: 2019-10-24
Filing date: 2019-10-24
Publication date: 2022-06-15
Also published as: EP3812112A1; FI3812112T3; FI20195915A1; CA3093892A1; EP3812112B1

Abstract

A hydraulic system for controlling a sawing apparatus adapted to cross-cut tree stems and including a swingable saw blade around which a saw chain is adapted to travel. The hydraulic system comprises control devices which are adapted to sense the fluid pressure of a first line (14), and to sense the fluid pressure of a pressure line (P), namely a first fluid pressure p1. The control devices are adapted to selectively reduce the third fluid pressure p3 of a pilot line (28), the third fluid pressure p3 being additionally dependent on a first fluid pressure difference between the fluid pressure of the first line (14) and the first fluid pressure p1 of the pressure line (P) in such a way that the third fluid pressure p3 decreases when the first fluid pressure difference decreases as a consequence of the fluid pressure of the first line (14) increasing while first and second valve arrangements (12, 20) are in their first states.

Description

HYDRAULIC SYSTEM FOR CONTROLLING A SAWING APPARATUS Technical Field The presented solution relates to a hydraulic system for controlling a sawing apparatus adapted to cross-cut tree stems.

The presented solution further relates to a sawing apparatus for cross- cutting tree stems and comprising a swingable saw blade around which a saw chain is adapted to travel, and a hydraulic circuit.

The presented solution further relates to a tree stem processing tool including a sawing apparatus for cross-cutting tree stems.

The presented solution further relates a mobile work machine.

Background Mobile work machines, forestry equipment and forestry machines, e.g. harvesters and forwarders, have an articulated boom and a tree stem processing tool at the tip of the boom.

The tool can be e.g. a harvester head, a felling head, or a harvesting and processing head.

The tool can be applied e.g. to cut standing trees, to process felled trees or to grab objects, such as logs or tree stems, and it is operated under the control of an operator of the work machine.

N The tool may have a sawing apparatus for cross cutting a standing tree N and/or a tree stem held in the tool.

The sawing apparatus is e.g. a O chain saw provided with a saw blade around which a saw chain travels = 30 when driven by an actuator, e.g. a hydraulic motor.

The actuator is = adapted to convert hydraulic pressure and fluid flow into torque and o rotational speed for driving the saw chain.

The sawing apparatus > includes an actuator, e.g. a hydraulic cylinder, for swinging the saw O blade for performing the cross-cutting.

The actuator is adapted to N 35 convert hydraulic pressure and flow into force and speed of the saw blade.

In a hydraulic system controlling the actuators, the saw chain on the saw blade is pressed against a tree stem with a force to crosscut the tree stem by means of the saw chain that is moving with a velocity. However, depending on the properties of the tree stem, the load on the motor and the saw chain pressing against the tree stem may increase and bring about a decrease in the velocity of the saw chain. The increase in the load implies an increased fluid pressure in a part of the hydraulic system and results in a decrease in the fluid flow.

The load on the saw chain decreases rapidly or disappears completely when the saw chain penetrates through the tree stem and the crosscutting is fully performed. However, immediately after this, the increased fluid pressure and hydraulic energy accumulated in the hydraulic system bring about a rapid, unwanted increase in the velocity of the saw chain, which may be risky.

A remedy is to have a pressure compensating flow control valve arrangement to keep the fluid flow supplied to the motor constant even if the load on the saw chain and the fluid pressure increases.

Operation of the valve arrangement is not optimal in a situation in which the operation involves delays, or the valve arrangement is saturated, i.e. in a state allowing a maximum fluid flow to pass via the valve arrangement to the motor to increase the velocity. An unwanted sudden increase in the velocity of the saw chain takes place when the crosscutting is fully performed even if the valve arrangement starts to N restrict the fluid flow.

N O A remedy is to control the fluid flow supplied to the hydraulic cylinder = 30 that is pressing the saw blade and the saw chain against the tree stem.

E Such a solution is presented in WO 2004/083653 A1.

= US 2004/0020561 A1 discloses a hydraulic system for controlling a 3 sawing apparatus including cylinder actuators and a circular saw blade.

N 35 In the hydraulic system of US 2004/0020561 A1, disclosing the | features of the preamble of claim 1, one valve arrangement is controlled such that a fluid flow is directed to one of the cylinder actuators to stop advancing and to start retracting the circular saw blade. US 4368763 A discloses a hydraulic system for controlling a sawing apparatus including actuators and a swingable saw blade around which a saw chain travels. In the hydraulic system of US 4368763 A a fluid flow is diverted to a tank line by way of a valve to slow down one of the actuators operating the saw blade. Summary The solution to be presented relates to overcoming one or more of the disadvantages noted above. — The hydraulic system according to the solution is presented in claim 1. The sawing apparatus according to the solution solution is presented in claim 13. The tree stem processing tool according to the solution is presented in claim 14. The mobile work machine according to the solution is presented in claim 15.

In the presented solution, the force with which the hydraulic cylinder presses the saw chain against the tree stem is controllably decreased to avoid the increase in the load on the saw chain and the unwanted decrease in the velocity of the saw chain. The unwanted sudden increase in the velocity of the saw chain immediately after crosscutting is avoided, or the velocity increases to an acceptable level only.

N N Brief Description of the Drawings > = 30 Figure 1 shows an exemplary mobile working machine applying the E presented solution.

LO 3 Figure 2 shows an exemplary tree stem processing tool applying the O presented solution. NN 35 Figure 3 shows an exemplary embodiment of the hydraulic system applying the presented solution.

Figure 4 shows another exemplary embodiment of the hydraulic system applying the presented solution. Figure 5 shows yet another exemplary embodiment of the hydraulic system applying the presented solution. Description of example embodiments Reference will now be made to the examples which are illustrated in the accompanying drawings. Wherever possible, the same or corresponding reference numbers will be used throughout the drawings to refer to the same or corresponding parts or features.

Fig. 1 shows an exemplary mobile work machine 100 in which the presented solution can be applied. The mobile work machine may be a forestry machine, for example a harvester for harvesting and processing timber or tree stems, as shown in Fig. 1, or a forwarder for transferring timber or tree stems. The mobile work machine 100 may be an excavator-based machine.

The mobile work machine 100 (also referred to herein as a machine, a mobile working machine, and a vehicle) comprises a frame 102 and an articulated boom 104 (also referred to herein as a boom) on the frame

102. The machine 100 may further comprise a cabin 104 with an operator’s station on the frame 102.

N N The frame 102 may be articulated and have two or more frame O sections connected one after the other by means of a controlled joint.

= 30 The frame 102 may be wheeled and supported by several wheels.

z Alternatively, the frame 102 may have an endless track arrangement, so i.e. a caterpillar track, for supporting the frame 102 and for driving the > machine 100.

O & 35 The boom 104 may be mounted on the frame 102 or a slewing apparatus 106 connected to the frame 102 for changing the orientation of the boom 104, or the frame 102 rotates in relation to the endless track arrangement. The boom 104 can be rotated about a rotation axis that is substantially vertical. The boom 104 may have two or more boom sections connected one after the other by means of joint arrangements controlled by means of one or several actuators, e.g. 5 hydraulic cylinders. Fig. 2 shows an exemplary tree stem processing tool 108 (also referred to herein as a tool) that may be connected to the boom 104. Preferably, the tool 108 is connected to the end of the boom 104.

The tool 108 may be rotatably connected to the boom 108 by means of an actuator 110, e.g. a rotary actuator or a rotator. By means of the actuator 110, the tool 104 suspended from the actuator 110 can be controllably rotated about a rotation axis that is oriented substantially vertically. The tool 108 may be a harvester head, a felling head, a harvesting and processing head, or a harvester head suitable for use as a log grapple. According to the example of Fig. 1, the tool 108 is a harvester head for harvesting and processing timber by first grabbing and felling a standing tree and then debranching and cross cutting the tree stem. The tool 108 may include a frame including tilting devices 122 enabling tilting of a housing of the tool 108. The tool 108 may have two or more arms 120 pivotally connected to the housing of the tool 108 for grabbing a standing tree, a log, or a tree stem e.g. from two opposite N sides. The arms 120 may be additionally constructed as blades for N debranching a tree stem held in the tool 108. <Q = 30 The tool 108 may comprise a feeding device 112 for transferring a tree z stem through the tool 108 while being held in the tool 108. The tree so stem is transferred in its longitudinal direction. The feeding device 112 > may include one or more feed wheels that contact the tree stem and 3 are adapted to rotate for transferring the tree stem. The tree stem is N 35 transferred for simultaneously debranching the tree stem by means of blades and/or for moving the tree stem to a position in which it is Crosscut.

The tool 108 has a sawing apparatus 114 for cross cutting a standing tree and/or a tree stem held in the tool 108. The sawing apparatus 114 is e.g. a chain saw provided with a swingable saw blade 116 around which a saw chain 118 travels when driven by an actuator, e.g. a rotary actuator or a motor. The motor may be a hydraulic motor adapted to convert hydraulic pressure and flow into torque and rotational speed for driving the saw chain 118. The sawing apparatus 114 includes an actuator for swinging the saw blade 116 for performing the cross- cutting, the actuator being adapted to convert hydraulic pressure and flow into force and speed of the saw blade 116. Fig. 3 shows an exemplary hydraulic system for controlling the sawing apparatus 114 that is adapted to cross-cut tree stems.

The hydraulic system according to the solution comprises a pressure line P; a tank line T; first and second actuators 10, 18; first and second electrically operated valve arrangements 12, 20; a pilot operated third valve arrangement 26; a fourth electrically operated valve arrangement 30; and control devices. The pressure line P supplies fluid under pressure, namely at a first fluid pressure pl. The pressure line P may be in the form of a branched circuit providing flows of fluid under pressure to various parts of the hydraulic system. A tank line T is adapted to receive fluid flowing from the actuators. The pressure line P may be in fluid communication with N a hydraulic pump providing the fluid under pressure. The tank line T N may be branched and is adapted to provide low backpressure. The O tank line T may be in fluid communication with a hydraulic reservoir to = 30 which the fluid is fed. The hydraulic system may further include drain = lines that provide very low backpressure and convey fluid to the so hydraulic reservoir. 2 O The first actuator 10 is a hydraulic motor to bring about a torgue for N 35 driving the saw chain 118 to move at a velocity and to crosscut a tree stem.

The first valve arrangement 12 is adapted to control a fluid flow supplied from the pressure line P to the first actuator 10. The fluid flows via a first line 14. For driving the first actuator 10, the first valve arrangement 12 includes a selectable first state which enables the flow of fluid under pressure from the pressure line P to the first line 14. The first valve arrangement 12 is electrically operated in such a way that the state can be selected with an input control signal that may provide proportional control of the fluid flow.

— The velocity of the saw chain 118 is dependent on the volume flow of the fluid supplied to the first actuator 10. The velocity increases with the increasing volume flow. The volume flow via the first valve arrangement 12 depends on a pressure difference between the pressure line P and the first line 14. The volume flow decreases with — the decreasing pressure difference. The fluid pressure in the pressure line P remains substantially constant during operation.

Therefore, an increasing load on the saw chain 118 may bring about an increase in the fluid pressure of the first line 14. The load on the saw chain 118 may vary according to the properties of the tree stem. The first actuator 10 provides an adeguate torgue for driving the saw chain

118. Thus, the pressure difference decreases and may have the unwanted conseguence that the flow of fluid to the first actuator 10 decreases and the velocity of the saw chain 118 decreases.

The load on the saw chain 118 decreases rapidly or disappears N completely when the saw chain 118 penetrates through the tree stem N and the crosscutting is fully performed. Immediately after this, the O increased fluid pressure in the first line 14 and hydraulic energy = 30 accumulated in the hydraulic system may bring about a rapid, z unwanted and considerable increase in the velocity of the saw chain so 118.

D O The first valve arrangement 12 may additionally include a selectable N 35 second state which disables the above-mentioned flow of fluid. In the second state, the first actuator 10 can be kept in a stopped state.

The first valve arrangement 12 may include one or more directional control valves that may be pilot operated or electrically operated.

The second actuator 18 is a hydraulic cylinder for driving the saw blade 116 to bring about a force pressing the saw chain 118 against the tree stem.

The second valve arrangement 20 is adapted to control a fluid flow supplied from the pressure line P to the second actuator 18. The fluid flows via a second line 22. For driving the second actuator 18 in a first direction, e.g. for extending or retracting the hydraulic cylinder, the second valve arrangement 20 includes a selectable first state which enables flow of fluid under pressure from the pressure line P to the second line 22. The first valve arrangement 20 is electrically operated in such a way that the state can be selected with an input control signal.

The second valve arrangement 20 may additionally include a selectable second state which disables the above-mentioned flow of fluid, or which enables a flow of fluid under pressure from the pressure line P to the third line 24 for retracting or extending the hydraulic cylinder.

In the first and second states, the second valve arrangement 20 may convey fluid from the actuator 18 to the tank line T.

Thus, the saw blade 116 is driven in an opposite, second direction away from the tree stem.

N Additionally, or alternatively, the second valve arrangement 20 may be N adapted to maintain backpressure in the actuator 18 for driving the saw O blade 116 in the second direction when the flow of fluid is disabled. = 30 z The second valve arrangement 20 may include one or more directional so control valves that may be pilot operated or electrically operated. 2 O The third valve arrangement 26 is pilot operated by means of a pilot N 35 line 28 and is adapted to maintain a predetermined second fluid pressure p2 in the fluid flow entering the second valve arrangement 20. The second fluid pressure p2 is reduced in relation to the first fluid pressure pl in such a way that the second fluid pressure p2 is dependent on third fluid pressure p3 of the pilot line 28 that is in fluid communication with the third valve arrangement 26. The fluid flow is adapted to enter the second valve arrangement 20 from the pressure line P via the third valve arrangement 26. The magnitude of the force pressing the saw blade 116 and the saw chain 118 against the tree stem is dependent on the second fluid pressure p2 present in the second actuator 18. The force increases — with the increasing fluid pressure. The load on the saw chain 118 also depends on the pressing force. The load increases with the increasing pressing force. Thus, the pressing force set to a high level by means of the second fluid pressure p2 may, as described above, have the unwanted consequence that the velocity of the saw chain 118 decreases. The magnitude of the pressing force is set by controlling the second fluid pressure p2 by means of the third valve arrangement 26 which is controlled by the third fluid pressure p3 of the pilot line 28.

The third valve arrangement 26 may include a function for limiting the pressure of the fluid flow. The third valve arrangement 26 may include a pressure limiting valve and/or a pressure reducing valve that is pilot operated and/or adjustable. The third valve arrangement 26 may provide proportional control in the form of a pressure control proportional valve.

N N The fourth valve arrangement 30 is controlled by a first electric input O control signal 32 and is adapted to be in fluid communication with the = 30 pilot line 28. The fourth valve arrangement 30 may be in fluid E communication with the pressure line P for directing fluid to the pilot so line 28. The fourth valve arrangement 30 is electrically operated and > provides proportional control of fluid pressure. Thus, the fourth valve 3 arrangement 30 is adapted to maintain the third fluid pressure p3 of the N 35 pilot line 28 at a predetermined maximum pressure level which depends on the magnitude of the first input control signal 32, being an electric signal.

Thus, the pressing force of the second actuator 18 is indirectly controlled by means of the pressure level of the third fluid pressure p3 of the pilot line 28 and the first input control signal 32.

The first input control signal 32 is dependent on control actions of an operator who is setting the predetermined maximum pressure level for the pilot line 28. The operator selects the third fluid pressure p3 by e.g. interacting with an electronic control unit 40 by means of a user interface. Thus, the operator sets the pressing force of saw blade 116 by means of the first input control signal 32. The fourth valve arrangement 30 may provide proportional control or include a directional control proportional valve and/or a restriction, or an orifice, in the pilot line 28, for inducing a pressure difference and for controlling the third fluid pressure p3. The electronic control unit 40 may be included in the fourth valve arrangement 30. The fourth valve arrangement 30 may be adapted to supply fluid from the pilot line 28 to a drain line, to maintain the third fluid pressure p3 at the predetermined maximum pressure level. The hydraulic system according to the solution may further comprise a sixth valve arrangement 16.

The sixth valve arrangement 16 is adapted to maintain a N predetermined substantially constant fluid flow while the first valve N arrangement 12 is in the first state. The operation is carried out in such O a way that the fluid flow is independent of the fluid pressure of the first = 30 line 14 and thereby any fluid pressure changes occurring in the first line = 14 are compensated for. Fluid flow received by the first actuator 10 and so arriving from the first line 14 is kept substantially constant. The fluid > flow enters the first valve arrangement 12 from the pressure line P via 3 the sixth valve arrangement 16. NN 35 The sixth valve arrangement 16 may include a pressure compensating flow control valve. The sixth valve arrangement 16 may include a restriction 46, or an orifice, across which the fluid flows, and the fluid pressure difference across the restriction 46 is sensed for the purpose of controlling the fluid flow.

The restriction 46 may be located upstream of the first valve arrangement 12 as shown in Fig. 3, or within a valve or valve element of the first valve arrangement 12, or in the first line 14 between the first actuator and the first valve arrangement 12. The sixth valve arrangement 16 may include pilot lines for sensing the fluid pressure difference. According to the presented solution, the hydraulic system further comprises control devices adapted to sense the level or magnitude of the fluid pressure of the first line 14, and to sense the level or — magnitude of the fluid pressure of the pressure line P, i.e. the first fluid pressure på. The control devices may include valve arrangements, valves, electronic control units, control algorithms, control signals, and pressure sensors, operably connected to each other and adapted to bring about the operation as described in the examples. The control devices are adapted to selectively reduce the third fluid pressure p3 of the pilot line 28, the third fluid pressure p3 being additionally dependent on a first fluid pressure difference. For example, one or more predetermined dependencies define the third fluid N pressure p3 as a function of the first fluid pressure difference. The one N or more predetermined dependencies may be realized in an electronic O control unit, e.g. an electronic control unit 40, for controlling elements = 30 and devices of the hydraulic system. = so The first fluid pressure difference is the pressure difference between > the fluid pressure of the first line 14 and the first fluid pressure p1 of the 3 pressure line P. The operation to reduce the third fluid pressure p3, as N 35 described above when reducing the pressing force, is brought about in such a way that the third fluid pressure p3 decreases when the first fluid pressure difference decreases as a conseguence of the fluid pressure of the first line 14 increasing. The operation takes place at least when the first and second valve arrangements 14, 20 are in their first states. During the operation, the first and second actuators 10, 18 are driven to crosscut the tree stem as described above. An advantage of the presented solution is that the pressing force of the second actuator 18 is decreased to avoid the increased load on the — saw chain 118 and the unwanted decrease in the velocity of the saw chain 118. An increase in the fluid pressure of the first line 14 is an indication of the decreasing velocity. Thus, the load on the saw chain 118 decreases and an increase in the — fluid pressure of the first line 14 is avoided. Thus, when cross-cutting the tree stem, excessive racing, i.e. sudden unintended acceleration, of the first actuator 10 and the saw chain 118 can be avoided when completing the cross-cutting. Inthe following, examples of the control devices are presented. As shown in Figs. 3 and 4, according to a first example of the solution, the control devices include a fifth valve arrangement 34 adapted to be in fluid communication with the pilot line 28. The fifth valve arrangement 34 may be adapted to controllably drain fluid from the pilot line 28 to decrease the third fluid pressure p3 to a level below the N predetermined maximum pressure level.

N O To accomplish this, the fifth valve arrangement 34 is adapted to sense = 30 the fluid pressure of the first line 14 and the fluid pressure of the z pressure line P, e.g. by means of pressure sensing lines, i.e. pilot lines. so The fifth valve arrangement 34 may provide proportional control and is > adapted to selectively reduce the third fluid pressure p3 in such a way 3 that the third fluid pressure p3 is dependent on the first fluid pressure difference mentioned above.

According to an example, the fifth valve arrangement 34 is further adapted to selectively increase the third fluid pressure p3 in such a way that the third fluid pressure p3 is additionally dependent on the first fluid pressure difference. Thereby, the third fluid pressure p3 increases when the first fluid pressure difference increases as a consequence of the fluid pressure of the first line 14 decreasing while the first and second valve arrangements 12, 20 are in their first states, the third fluid pressure p3 not exceeding the predetermined maximum pressure level. — As shown in Fig. 4, according to a first option of the first example, the fifth valve arrangement 34 may be pilot operated and includes either a first pilot line 36 (see Fig. 3) that is in fluid communication with the first line 14 for sensing the fluid pressure of the first line 14, or a second pilot line 38 that is in fluid communication with the pressure line P for sensing the fluid pressure of the pressure line P. Additionally, the fifth valve arrangement 34 may include an electrically operated proportional control directional valve. The fifth valve arrangement 34 may comprise a first pressure sensor 42 for sensing the fluid pressure of the first line 14, or a second pressure sensor 444 (see Fig. 5) for sensing the fluid pressure of the pressure line P. In this option, the fifth valve arrangement 34 may comprise an electronic control unit, e.g. the electronic control unit 40, operably connected to the first pressure sensor 42 or the second pressure sensor 44, the electronic control unit being adapted to control the fifth N valve arrangement 34 by a second input control signal 46 that is N dependent on the determined fluid pressure of the pressure line P or O on the determined fluid pressure of the first line 14. The second input = 30 control signal 46 is generated by a control algorithm running in the z electronic control unit and based on one or more predetermined so dependencies.

D O The fifth valve arrangement 34 thus comprises one pilot line and one N 35 pressure sensor and is electronically controlled by the second input control signal 46 representing a pressure level. The fifth valve arrangement 34 may be internally adapted to balance forces generated by both the fluid pressure in the pilot line and the second input control signal 46 driving e.g. a solenoid. The difference between the forces represents the first fluid pressure difference. As shown in Fig. 3, according to a second option of the first example, the fifth valve arrangement 34 may be pilot operated and includes both the first pilot line 36 for sensing the fluid pressure of the first line 14, and the second pilot line 38 for sensing the fluid pressure of the pressure line P.

The fifth valve arrangement 34 thus comprises two pilot lines and the difference between the fluid pressures in the two pilot lines define the first fluid pressure difference. The fifth valve arrangement 34 may be internally adapted to balance forces generated by the fluid pressures in — the pilot lines. The difference between the forces represents the first fluid pressure difference. The fifth valve arrangement 34 may include a pilot operated directional valve. Based on the second option shown in Fig 4, according to a third option of the first example, the fifth valve arrangement 34 may be electrically operated and/or provide proportional control, and it may include an electrically operated proportional control directional valve. In this option, see Fig. 4, the fifth valve arrangement 34 comprises a — first pressure sensor 42 for sensing the fluid pressure of the first line 14, and a second pressure sensor 44 (see Fig. 5) for sensing the fluid N pressure of the pressure line P at the first fluid pressure p7.

N O The fifth valve arrangement 34 may further comprise an electronic = 30 control unit, e.g. the electronic control unit 40, operably connected to z the first and second sensors 42, 44, the electronic control unit being so adapted to control the fifth valve arrangement 34 by the second input > control signal 46. The second input control signal 46 is dependent on 3 the first fluid pressure difference determined, the second input control N 35 signal 46 being generated by a control algorithm running in the electronic control unit and based on one or more predetermined dependencies.

As shown in Fig. 5, according to a second example of the solution, the control devices comprise a first pressure sensor 42 for sensing the fluid pressure of the first line 14, and a second pressure sensor 44 for sensing the fluid pressure of the pressure line P. The first and second pressure sensors 42, 44 may be included in the fourth valve arrangement 30. In the second example, the control devices, or the fourth valve arrangement 30, may further comprise an electronic control unit, e.g. the electronic control unit 40, operably connected to the first and second sensors 42, 44, the electronic control unit being, as described above, adapted to control the fourth valve arrangement 30 by the first input signal 32. The first input signal 32 being thus additionally = dependent on the determined first fluid pressure difference, the first input signal is generated by a control algorithm running in the electronic control unit and based on one or more predetermined dependencies. Control actions based on the first fluid pressure difference override control actions of an operator when adjusting the third fluid pressure pS. Additionally, the first input control signal 32 is dependent on control actions of an operator for setting the predetermined maximum level for the third fluid pressure p3 of the pilot line 28. The operator sets the — third fluid pressure p3 by interacting with the electronic control unit by means of a user interface. Thus, the operator sets the pressing force of N the saw blade 116 by means of the first input control signal 32.

N O The electronic control unit may be a programmable microprocessor- = 30 based device with a memory device and associated computer program z code, for generating input control signals to responsively control the so devices and valve arrangements. The control unit may have a 3 distributed configuration with several subunits. > & 35 Other components necessary for the basic functioning of the presented hydraulic circuit and for controlling flows of fluid in the presented system may be added to the solution presented in the Figures.

Furthermore, each valve arrangement and control device realize the operations and functions that are described above. Elements needed to realize the valve arrangement, or the control device, are widely known and may include one or more valves of various types, based on various operating principles, e.g. valves applying proportional or servo control, spool valves, or cartridge valves. The graphical symbols shown in the Figures to represent e.g. the valve arrangements do not limit the types of valves used but merely show an example how to realize the — operation and functions of the hydraulic circuit. The verbs "to comprise" and "to include" are used in this document as open limitations that neither exclude nor require the existence of features that are not cited. Furthermore, it is to be understood that the use of "a" or "an", i.e. a singular form, throughout this document does not exclude a plurality, unless where specifically mentioned. In the description, numerous specific details are set forth in order to provide a thorough understanding of the present solution. It is to be understood that the examples of the solution disclosed are not limited to the structures disclosed herein, but are extended to equivalents thereof as would be recognized by those skilled in the relevant art. The solution is not limited solely to the above-presented embodiments, but it can be modified within the scope of the appended claims.

N N O

N > Nn

I =

LO O

LO o

O N

Claims

Patenttivaatimukset:

1. Hydraulinen järjestelmä puunrunkojen katkaisuun sovitetun saha- laitteiston ohjaamiseksi, joka hydraulinen järjestelmä käsittää: — painelinjan (P), joka on sovitettu syöttämään paineistettua, nimittäin ensimmäisessä nesteen paineessa p17 olevaa nestettä; — säiliölinjan (T), joka on sovitettu vastaanottamaan toimilaitteista virtaavaa nestettä; — ensimmäisen toimilaitteen (10), joka on hydraulimoottori vään- tömomentin aikaansaamiseksi sahalaitteiston käyttämiseksi liikkumaan jollakin nopeudella ja katkaisemaan puunrunko; — ensimmäisen sähkötoimisen venttiilijärjestelyn (12), joka on sovitettu ohjaamaan painelinjasta (P) ensimmäisen linjan (14) kautta ensimmäiseen toimilaitteeseen (10) syötettävää nestevirtausta, jolla ensimmäisellä venttiilijärjestelyllä (12) on: — valittavissa oleva ensimmäinen tila paineistetun nesteen päästämiseksi virtaamaan painelinjasta (P) ensimmäiseen linjaan (14) ensimmäisen toimilaitteen (10) käyttämiseksi; — toisen toimilaitteen (18), joka on hydraulisylinteri sahalaitteiston käyttämiseksi aikaansaamaan sahalaitteistoa puunrunkoa vasten puris- tava voima,

N N — toisen sähkötoimisen venttiilijärjestelyn (20), joka on sovitettu 3 ohjaamaan painelinjasta (P) toisen linjan (22) kautta toiseen toimi- S 30 laitteeseen (18) syötettävää nestevirtausta, jolla toisella venttiilijärjeste- z lyllä (20) on: so — valittavissa oleva ensimmäinen tila paineistetun nesteen > päästämiseksi virtaamaan painelinjasta (P) toiseen linjaan (22) toisen 3 toimilaitteen (18) käyttämiseksi: N 35 — kolmas venttiilijärjestely (26), joka on sovitettu ylläpitämään toiseen venttiilijärjestelyyn (20) tulevassa nestevirtauksessa ennalta määrättyä nesteen painetta p2, joka toinen nesteen paine p2 on alempi kuin ensimmäinen nesteen paine p17, — ja nestevirtaus on sovitettu tulemaan toiseen venttiili- järjestelyyn (20) painelinjasta (P) kolmannen venttiilijärjestelyn (26) kautta;

— ohjauslaitteita, jotka on sovitettu tunnistamaan ensimmäisen linjan (14) nesteen paine; tunnettu siitä, että:

— sahalaitteisto käsittää kääntyvän terälevyn, jonka ympäri saha- ketju on sovitettu kulkemaan, ja ensimmäinen toimilaite (10) on sovitet- tu käyttämään sahaketjua ja toinen toimilaite (18) on sovitettu käyttä-

mään terälevyä sahaketjun painamiseksi puunrunkoa vasten;

— kolmas venttiilijärjestely (26) on esiohjattu, ja toinen nesteen paine p2 on lisäksi riippuvainen kolmannesta nesteen paineesta p3 esiohjauslinjassa (28), joka on nesteyhteydessä kolmannen venttiili-

— järjestelyn (26) kanssa;

— hydraulijärjestelmä käsittää neljännen sähkötoimisen venttiili- järjestelyn (30), jota ohjataan ensimmäisellä sähköisellä ohjaus- tulosignaalilla (32) ja joka on sovitettu olemaan nesteyhteydessä esi-

— ohjauslinjan (28) kanssa, — joka neljäs venttiilijärjestely (30) on sovitettu pitämään

N esiohjauslinjan (28) kolmas nesteen paine p3 ennalta määrätyllä mak- N simipainetasolla, joka riippuu ensimmäisen ohjaustulosignaalin (32) 3 voimakkuudesta; ja S 30 = — hydraulijärjestelmä käsittää lisäksi: so — ohjauslaitteita, jotka on sovitettu tunnistamaan paine- > linjan (P) nesteen paine, nimittäin ensimmäinen nesteen paine p17, 3 — jotka ohjauslaitteet on sovitettu alentamaan selektiivisesti N 35 — esiohjauslinjan (28) kolmatta nesteen painetta p3, joka kolmas nesteen paine p3 on lisäksi riippuvainen ensimmäisen linjan (14) nesteen pai-

neen ja painelinjan (P) ensimmäisen nesteen paineen p17 välisestä ensimmäisestä nesteen paine-erosta siten, että kolmas nesteen paine p3 alenee, kun ensimmäinen nesteen paine-ero alenee sen seurauk- sena, että ensimmäisen linjan (14) nesteen paine nousee, kun ensim- mäinen ja toinen venttiilijärjestely (12, 20) ovat ensimmäisessä tilas- saan.

2. Patenttivaatimuksen 1 mukainen hydraulijärjestelmä, jossa ohjaus- laitteissa on: — viides ohjausventtiilijärjestely (34), joka on sovitettu olemaan — nesteyhteydessä esiohjauslinjaan (28), tunnistamaan ensimmäisen lin- jan (14) nesteen paine ja tunnistamaan painelinjan (P) nesteen paine, — joka viides venttiilijärjestely (34) on sovitettu alentamaan esiohjauslinjan (28) kolmatta nesteen painetta p3 selektiivisesti siten, että kolmas nesteen paine p3 on riippuvainen ensimmäisestä nesteen paine-erosta.

3. Patenttivaatimuksen 2 mukainen hydraulijärjestelmä, jossa viides venttiilijärjestely (34) on lisäksi sovitettu nostamaan esiohjauslinjan (28) kolmatta nesteen painetta p3 selektiivisesti siten, että kolmas nesteen paine p3 on lisäksi riippuvainen ensimmäisestä nesteen paine-erosta eikä kolmas nesteen paine p3 ylitä ennalta määrättyä maksimipaine- tasoa.

4. Patenttivaatimuksen 2 tai 3 mukainen hydraulijärjestelmä, jossa vii- — des venttiilijärjestely (34) on esiohjattu ja käsittää: — (i) ensimmäisen esiohjauslinjan (36), joka on nesteyhteydessä N ensimmäiseen linjaan (14) ensimmäisen linjan (14) nesteen paineen N tunnistamiseksi, tai 3 — (ii) toisen esiohjauslinjan (38), joka on nesteyhteydessä paine- S 30 linjaan (P) painelinjan (P) nesteen paineen eli ensimmäisen nesteen z paineen p7 tunnistamiseksi. = 5. Jonkin patenttivaatimuksen 2-4 mukainen hydraulijärjestelmä, jossa 3 viides venttiilijärjestely (34) käsittää lisäksi: N 35 — (i) ensimmäisen paineanturin (42) ensimmäisen linjan (14) nes- teen paineen tunnistamiseksi tai

— (ii) toisen paineanturin (44) painelinjan (P) nesteen paineen tunnistamiseksi, sekä — sähköisen ohjausyksikön (40), joka on liitetty toiminnallisesti ensimmäiseen ja toiseen anturiin (42, 44) ja sovitettu ohjaamaan viidet- tä venttiilijärjestelyä (34) toisen ohjaustulosignaalin (46) avulla, joka on riippuvainen (i) määritetystä painelinjan (P) nesteen paineesta tai (ii) määritetystä ensimmäisen linjan (14) nesteen paineesta, ja joka toinen ohjaustulosignaali (46) on muodostettu sähköisessä ohjausyksikössä (40) ajettavalla ohjausalgoritmilla.

6. Patenttivaatimuksen 2 tai 3 mukainen hydraulijärjestelmä, jossa vii- des venttiilijärjestely (34) on esiohjattu ja käsittää: — ensimmäisen esiohjauslinjan (36), joka on nesteyhteydessä ensimmäiseen linjaan (14) ensimmäisen linjan (14) nesteen paineen — tunnistamiseksi, ja — toisen esiohjauslinjan (38), joka on nesteyhteydessä paine- linjaan (P) painelinjan (P) nesteen paineen tunnistamiseksi.

7. Jonkin patenttivaatimuksen 2, 3 tai 6 mukainen hydraulijärjestelmä, — jossa viides venttiilijärjestely (34) käsittää: — ensimmäisen paineanturin (42) ensimmäisen linjan (14) nes- teen paineen tunnistamiseksi ja — toisen paineanturin (44) painelinjan (P) nesteen paineen tun- nistamiseksi, — sähköisen ohjausyksikön (40), joka on liitetty toiminnallisesti ensimmäiseen ja toiseen paineanturiin (42, 44) ja sovitettu ohjaamaan N viidettä venttiilijärjestelyä (34) toisen ohjaustulosignaalin (46) avulla, N joka on riippuvainen määritetystä ensimmäisestä nesteen paine-erosta 3 ja joka toinen ohjaustulosignaali (46) on muodostettu sähköisessä S 30 — ohjausyksikössä (40) ajettavalla ohjausalgoritmilla. = so

8. Jonkin patenttivaatimuksen 2-7 mukainen hydraulijärjestelmä, jossa > viides venttiilijärjestely (34) käsittää sähkötoimisen suuntaventtiilin tai 3 esiohjatun suuntaventtiilin. N 35

9. Patenttivaatimuksen 1 mukainen hydraulijärjestelmä, jossa ohjaus- laitteissa on:

— ensimmäinen paineanturi (42) ensimmäisen linjan (14) nesteen paineen tunnistamiseksi, — toinen paineanturi (44) painelinjan (P) nesteen paineen tunnis- tamiseksi, ja — sähköinen ohjausyksikkö (40), joka on liitetty toiminnallisesti ensimmäiseen ja toiseen anturiin (42, 44) ja sovitettu ohjaamaan neljät- tä venttiilijärjestelyä (30) ensimmäisen ohjaustulosignaalin (32) avulla, joka on lisäksi riippuvainen määritetystä ensimmäisestä nesteen paine- erosta ja joka ensimmäinen ohjaustulosignaali (32) on muodostettu — sähköisessä ohjausyksikössä (40) ajettavalla ohjausalgoritmilla.

10. Jonkin patenttivaatimuksen 1-9 mukainen hydraulijärjestelmä, jossa neljäs venttiilijärjestely (30) käsittää sähkötoimisen, proportio- naaliohjatun suuntaventtiilin, joka on sovitettu ohjattavaksi ensimmäi- sen ohjaustulosignaalin (32) avulla.

11. Jonkin patenttivaatimuksen 1-10 mukainen hydraulijärjestelmä, joka hydraulijärjestelmä käsittää lisäksi: — kuudennen venttiilijärjestelyn (16), joka on sovitettu pitämään — ensimmäisen venttiilijärjestelyn (12) ensimmäisessä tilassa ennalta määrätty, oleellisesti vakio nestevirtaus siten, että nestevirtaus on riip- pumaton ensimmäisen linjan (14) nesteen paineesta ja ensimmäisessä linjassa (14) tapahtuvat nesteen paineen muutokset kompensoidaan, — ja nestevirtaus on sovitettu tulemaan ensimmäiseen venttiili- — järjestelyyn (12) painelinjasta (P) kuudennen venttiilijärjestelyn (16) kautta.

N N 12. Jonkin patenttivaatimuksen 1-11 mukainen hydraulijärjestelmä, 3 joka hydraulijärjestelmä käsittää lisäksi sähköisen ohjausyksikön (40), S 30 joka on liitetty toiminnallisesti neljänteen venttiilijärjestelyyn (30), säh- = köisessä ohjausyksikössä (40) ajettavalla ohjausalgoritmilla muodoste- so tun ensimmäisen ohjaustulosignaalin (32) lähettämiseksi käyttäjän > ohjaamana.

O | 35 13. Sahalaitteisto (114) puunrunkojen katkaisemista varten, joka saha- laitteisto käsittää kääntyvän terälevyn (116), jonka ympäri on sovitettu kulkemaan sahaketju (118), sekä jonkin patenttivaatimuksen 1—12 mukaisen hydraulijärjestelmän.

14. Puunrunkojen käsittelyväline (108), joka käsittää sahalaitteiston (114) puunrunkojen katkaisemista varten, joka sahalaitteisto (114) käsittää kääntyvän terälevyn (116), jonka ympäri on sovitettu kulke- maan sahaketju (118), sekä jonkin patenttivaatimuksen 1-12 mukaisen hydraulijärjestelmän.

15. Liikkuva työkone (100), joka käsittää rungon (102), nivelöidyn puo- min (104), joka on rungolla, ja nivelöityyn puomiin liitetyn puunrunkojen käsittelyvälineen (108), joka käsittää sahalaitteiston (114) puunrunko- jen katkaisemista varten, joka sahalaitteisto (114) käsittää kääntyvän terälevyn (116), jonka ympäri on sovitettu kulkemaan sahaketju (118), ja jonkin patenttivaatimuksen 1-12 mukaisen hydraulijärjestelmän.

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