SE532733C2 - Drive systems for the feeders' hydraulic motors in the branch and cutter head in a harvester - Google Patents

Description

533: F33 engine part that produces one revolution volume in the four-capacity engine connected directly in series with a traditional hydraulic motor. When the drive condition of the fl recapacity engine changes from maximum rev volume to, for example, half rev volume, the speeds of the hydraulic motors throughout the system change at the same time.

With, for example, half the rev volume, a smaller torque, but a higher speed, is achieved with fl capacity capacity motor. Some of the working-phase pistons in the hydraulic motor with radial pistons are exposed to so-called rest pressure and the actual fl fate of oil with working pressure takes place in the condition in question only via certain working-phase cylinders and pistons, whereby the amount (Q l / s) of the to these controlled pressurized media rises, which leads to an increase in the rotor speed.

The other engines are similarly fed a larger amount of oil per unit time, whereby their speeds also increase. A consequence of this, however, is that the ratio between the mutual speeds of the motors remains unchanged, whereby no slimming occurs during the feeding of the tree.

When the drive condition of the fl capacity is reversed to full speed, the other engine part of the mot capacity is also switched on. The first motor part Selection of the fl capacity capacity is then connected in series with a standard hydraulic motor and the second motor part Va; of the multi-capacity motor is connected in parallel with this According to the invention, it has been realized to explicitly use a radial piston hydraulic motor to provide a motor with variable capacity.

A basic principle in the solution according to the invention is that the working pressure in the system is observed in the inlet duct A1 for oil to the multi-capacity engine which is connected in series with the ordinary hydraulic engine. When the working pressure drops below a certain tolerance range, one revolution volume Va is switched off; in the fl capacitance motor, wherein the multi-capacity motor and the cylinders Va in this drive state Va; is in pure series with the connected ordinary hydraulic motor, whereby no slippage can occur at the tree feed. The speed adjustments of the driven high-capacity hydraulic motors 1, 2 can take place independently of each other. 10 15 20 25 30 532 733 The inventive drive system for the hydraulic motors of the feeder devices in the pruning and cutting head of a deforestation machine is characterized by what is stated in the claims.

The invention is described in the following with reference to some advantageous embodiments of the invention shown in the figures in the accompanying drawings. However, it is not intended to limit the invention to these embodiments only.

FIG. 1A shows a prior art harvester head where a hydraulic system according to the invention can be applied.

FIG. 1B shows a prior art drive system for the drive rollers in a harvester.

FIG. 2A shows an inventive drive system for the hydraulic motors of a harvester.

FIG. 2B shows a drive condition in which one fl capacitance motor operates at half speed, FIG. ZC shows a setting of the system where both multi-capacity motors 1 and 2 operate with partial rpm, for example half rpm.

FIG. 3 schematically shows a slip protection arrangement with feedback from the working pressure circuit.

FIG. 4A and 4B show two different longitudinal sections of a radial piston hydraulic motor acting as a full capacity motor for showing the channels in the motor. 10 20 20 30 30 532? 33 FIG. 5 shows the simplest embodiment of the inventive drive system comprising only one overcapacity motor and one other motor connected thereto, which is advantageously a standard hydraulic motor.

FIG. 6 shows a cross section of a radial piston hydraulic motor for showing the radial piston structure and the waveforms of the cam ring connecting to the piston structure.

FIG. 1A shows the principle of construction of a harvester head according to the prior art. A harvester head or a pruning and cutting head M in a deforestation machine comprises a frame N, which can be connected to the deforestation machine or harvester via not shown movable arms.

The harvester head M comprises cutting knives 01 and 02 connected to the body as well as feed rollers dj, d2, d; and then. The feed rollers d; and D; can be pressed by means of arms against a tree to be fed, while the feed rollers dg and di; are connected to hydraulic motors attached to the body of the harvester head. The feed rollers dj and d; in the construction according to the invention, on the other hand, are connected to fl capacitance hydraulic motors 1 and 2, which are movable in relation to the body N of the harvester head by means of arms Tj, T; and controls. A saw R is arranged at the bottom of the harvester head shown in the figure for cutting the tree trunk in desired lengths. The tree to be felled is gripped by means of the feed rollers and it is sawn off with the saw and then the tree is removed at the inventive solution by means of the four hydraulic motors by rotation of the feed rollers di, dg, d; and d4, the tree being displaced past the cutting edges 01 and 0; and the twigs of the tree are cut off, the tree being pruned.

A hydraulic system 100 according to the invention is used, for example, in connection with that in FIG. 1A showed the prior art harvester head 11.

The harvester head comprises the hydraulic motors 3 and 4 and the fl capacity capacitor motors 1 and 2 on the movable arms Tj and Tg. The rollers 10 15 20 25 30 532? 33 d3 and d4 are advantageously located next to each other and the feed means, advantageously the rollers d1 and d; are correspondingly adjacent next to each other in connection with the multi-capacity motors 1 and 2.

FIG. 1B shows a prior art hydraulic system for the pruning and cutting head M of a harvester.

FIG. 1B schematically shows a generally known way of providing slip protection and control of the tree feed speed in harvester heads with four feed rollers.

Since the lower motors in Figure 1B are mechanically coupled to each other, neither side can slip.

The engine speed is controlled with a proportional valve. The motors must have a certain speed to give a sufficiently large torque. At high speeds, these rev volumes do not change, so large and expensive pumps are required to obtain a sufficiently large torque.

One way is to use engines with fl your speeds. When steering in this traditional way, all motors must be multi-speed motors, which is a costly solution. In addition, the amount of oil in the engines located one after the other must be approximately equal in size, since the engines are connected in series. Otherwise, the feed speeds of the rollers driven by the upper and lower motors would be different, which is of course not desirable. The volumes of all engines must, of course, be changed simultaneously.

In the following, starting from FIG. 2A shows a control and drive system 100 according to the invention 100 for the tree feeding devices in the pruning and cutting head M of a harvester. The system enables changes in the feed speed and prevents slimming of the motors. The arrangement comprises at least four pressure medium-driven, wood feed feed motors 1, 2, 3 and 4, advantageously hydraulic motors, each of which is arranged to drive and rotate a feed member, such as a feed roller d1, dz, d; and d4. The rollers are intended to abut against a tree trunk and to feed the tree trunk through said head for cutting the tree branches with the cutting knives (in FIG. 1A).

FIG. 2A schematically shows that a pressure medium can be led to the hydraulic motors 1, 2, 3 and 4 through a channel 11 and led back from them through a channel B. A part 1, 2 of said feed motors are capacity capacitors, whereby for these two motors 1, 2 at least a first revolution volume Va1 and at least a second revolution volume Va, + Vag can be selected. There are a first and a second base or pressure connection or input At, A2 for working pressure to the hydraulic motors 1 and 2 to provide two capacitances. The first base connections A1 to the fl capacitance motors 1, 2 are connected in series with the base connections to the other motors 3, The second base connections A2 to the capacitance motors 1, 2 are connected separately as a second connection for pressurized medium, such as oil, the input to said connection going from a dry branch point C1 on the input side of the other motors 3 and 4, i.e. oil fl fate passes the standard hydraulic motors 3 and 4.

The third connections A3, and A4 to the fl capacity capacitors are in turn connected to the channel B.

The coupling arrangement further comprises a functional means 50, such as a device with a valve slide, for coupling two different vanes / volumes or two different so-called driving license. From an economic point of view, it is advantageous that the motors 3 and 4 are not so-called fl speed motors. Despite this, in the system with the same available capacity from a pump P1, different speeds and different torques are achieved at each capacity. 10 15 20 25 30 532 F33 FIG. 2A shows a state where the system operates at full volume i.e. with the lowest speed and maximum torque. In connection with the invention, the good sides of both series connection and parallel connection have been considered. The engine 2 is connected in series with the engine 4 and with respect to the cylinder group Va; also connected in parallel with this. The motor 1 is correspondingly connected in series and in parallel with the motor 3. Through the parallel connection, the large power of the grain is achieved with the motor and through the series connection in turn slip protection.

The invention allows the use of different types of overcapacity hydraulic motors.

The multi-capacity hydraulic motors 1, 2 are advantageously radial piston hydraulic motors, which comprise pistons V and on these core rollers or pressure rollers 64, which are arranged to abut against a cam ring 65. The motor 10 comprises a distributor or distribution valve 60, with which a pressurized medium, such as oil, can be phased. brought to each piston V to place the piston in either the working phase or the oil return phase. In or in connection with the fl capacity capacity there is an arrangement, with which some Va; of the pistons V can be dried in the rest phase by displacing a slide 51 in a control valve 50, whereby oil under working pressure can be conveyed only to a part Va1 of the pistons, whereby their speed of movement increases and the rotational speed of the engine 1.2 increases correspondingly, but the torque of the hydraulic motor sinks.

As can be seen from the schematic figure 2A, the hydraulic system 100 comprises a directional valve 10, in which a central block 10a2 is a blocking block, the pressurized medium not being led from the pump P1 to the system 100 and also the return channel being closed. The left block l0a1 in the clock causes pressurized oil to flow (arrow S1) to the system 100 through the channel ll. As can be seen from the figure, the channel 11 is branched into branch channels 12 into a channel system M1 and a channel system M2.

The branch channel 12 is branched at a point C1 into a branch channel AO and a branch channel A1. The arrangement is the same for both motors 1 and 2. The channel A0 leads to the hydraulic motor 3 and from this a channel A1 leads on to the cylinder group V81 in the capacity motor 21,2. The channel A1 thus leads to these determined cylinders and pistons Va1 in the capacity motor 1 or 2 and the branch channel A2 leads directly to the other cylinders and pistons Va; in the fl capacity capacity l. The engine speed can thus be changed depending on the supply of pressurized medium either to the cylinder group Va1 + Va; or only to the cylinder group Va; in the engine 1.

From the channel A1 a control connection C10 goes to a functional member 50, which according to the pressure can close the channel A2 or keep it open. Thus, if the pressure drops in the channel A1 below a certain limit value, the drive state Va, + Va is switched off; and the drive state is switched on. certain cylinders / pistons Va; disconnected from operation in working phase and only certain cylinders / pistons Va; is in use. In this way the speed of the engine is changed 1. The state Va; means partial speed volume and the condition Vai + Val full speed volume. From the motors 1 and 2, return channels A3 and A4 lead to the common return channel B. When the block 10a3 in the directional valve 10 is connected, the direction of rotation of the hydraulic motor is reversed. When the block IOa; in the directional valve 10 is engaged, the oil in it circulates with the arrow S; shown direction and when block 102.2 is connected, the system is plugged in / closed.

In FIG. 2B, the motor 1 is connected at partial volume. This means that the feed speed of all motors increases at the same capacity of the pump P1. However, their mutual speed ratios remain unchanged. Thus, no slippage can occur as would be the case when speed differences arise.

In FIG. 2C, motors 1 and 2 are connected at subvolume because they have shown a tendency to slip. The motors are then connected in series with motors 3 and 4 and cannot slip.

The motor 2 and motor 1 have a built-in anti-slip function. If the pressure in the channel A1 drops to a sufficiently low value, this indicates a danger of slipping of the motor 1 and / or 2. In such a case, the volume Va is switched off; automatically and the engine l 10 15 20 25 30 532 'F33 and / or 2 starts working with the partial volume. Motors 1 and 2 can no longer slip after this, as they are in pure series with motors 3 and 4.

In the system according to the invention, either of the multi-capacity motors 1 and 2 or each can be regulated to partial speed volume states or full speed volume states independently of each other.

FIG. 3 schematically shows the hydraulic diagram of a system in connection with an inventive capacity motor. According to the invention, the pressure is conducted from a channel A1 as control pressure to a function means, such as a control valve 50, for setting the control valve to a position which provides a certain driving state of the fl capacitance motor 1 or 2. In a state where the fl capacitance motor is connected to, for example, half volume Var is the group Va; as shown in the figure disconnected from the friction with working pressure. Such a situation arises when the pressure drops in the channel A1, for example during slipping. In this case, the multi-capacity engine is switched to partial volume, for example half volume, when the piston / cylinder group Va; connected to function with so-called resting pressure, the hydraulic oil controlled for this group circulating with resting pressure in an internal circuit Bi, F in the engine via the cylinders Vaz in question. Said series connection and said circulation of the same amount of oil via both engines i.e. via the conventional hydraulic motor located in the figures below and via the pistons Vai operating at half volume in the upper capacity motor shown in the figures guarantees that the motors 1, 3 and 2, 4 are in series and slippage between them is prevented. The fact that some Va; of the volume is disconnected (from the pistons / cylinders in the figure) leads to this amount of oil having to be carried to the other parts of the system. This in turn leads to the speeds of all motors 1, 2, 3 and 4 increasing in the same proportion.

The functional means 50, such as a valve, with which the operating state of the hydraulic motor 1, 2 can be selected, can also be located outside the motor structure 1, 2. Advantageous, however, is such an embodiment where the functional means 50 for selecting the turning volume in the hydraulic motor 1 is built into the motor 1 itself. In the following, the operating principle of the system 100 is described in more detail from FIG. In FIG. 3 shows the operating means, with which the rotational volume of the multi-capacity motor 1 is regulated and with which thus also the anti-slip protection of the rollers d1, dg, d; and d4 for feeding trees through the harvester head M is regulated.

The system 100 thus comprises the operating means 50, advantageously a valve device, which, depending on the pressure prevailing in one channel A1 for working pressure to the motor 1, regulates the rotational volume of the multi-capacity motor 1 and closes certain cylinders Va if necessary; and switches these on when the working pressure prevailing in the channel A1 increases again. In the figure, the particular working cylinder group in the fl capacity capacitor 1 is denoted by Va1 and the other other cylinders are denoted by Vaz. The pressurized medium is led as shown in the figure through the channels A1 and A2 to the radial piston hydraulic motor 1. The pressurized medium is led through the channel A1 to the cylinder group Va1 and the second working pressure channel A2 passes through the function means, advantageously a valve 50. When the block 50a2 in the valve 50 is actively forms the cylinder group Va; a closed system. Thus, no pressurized medium is led to the system through the channel A; due to the inlet being closed. The block 50a2 in the valve 50 always joins the channel A1 to the cylinder groups Va1 (when the block is active) and closes the second channel A2 for working pressure if the pressure in the channel A1 drops. To the operating means 50, advantageously a control valve, leads a pressure feedback channel C111 from the pressure channel A1. From the channel A1 a feedback channel C111 thus goes to the valve 50, which shuts off the other cylinders Va; from the working pressure against the force of a spring J, if the pressure in the channel A1 drops sufficiently low. The valve device 50 can advantageously be formed by a guide slide 51 with piston-like latches G1, G2, G3 in a bore 52 in the hydraulic motor. The spring J is located at the end of the guide slide 51.

Functional means of another type are also possible. The function member 50 is advantageously located in the motor itself, but in an embodiment can also be located outside it. 10 15 20 25 30 532 'F33 ll The cylinders Val in the motor 1 are connected in series with the ordinary motor 3 and the cylinders Val in the multi-capacity motor 2 are correspondingly connected in series with the ordinary motor 4. The ordinary motors 3 and 4 can also be mechanically connected to each other.

FIG. 3 also shows a directional valve 70, which is solenoid-operated against the force of a spring J111. When the block 70a in the directional valve is in the active position as shown in the figure, the pressure prevailing in the line C111 is sensed, this being led to the end of the slide 51 in the operating means 50, advantageously a valve device, to actuate the valve slide against the force of the spring I. in the directional valve 70 is in the active position, ie when no control voltage is applied to the solenoid, the connection from the pressure channel C111 to the slide is closed, the spring I in the operating means 50 displacing the slide to a position where the group Va; is switched off and the engine is driven at a higher speed.

FIG. 4A and 4B show two longitudinal sections of the same radial piston hydraulic motor 1, 2 for illustrating the motor constructions. The pressure channels A1, A2 are connected via the distributor or distribution valve 60 to the piston bodies 61 and to the cylinders / pistons Val, Vaz. The shaft 62 does not rotate in the embodiment according to the figure. The jacket 63 rotates while the pressure rollers 64 connected to the pistons abut against the wave-united cam ring 65. When the corrugated core ring 65 is set in rotation, the motor jacket and the associated distribution valve 60 also rotate, which distributes pressurized oil in the correct phase to the working phase the pistons and removes oil at the right moment from the pistons.

The return connection from the cylinders Val, Va; goes via channels in the distributor 60 to channels in the shaft and out of the system. The operating means 50 comprises the slide 51 in the bore 52 in the shaft 62. The slide can be displaced in the bore S2 towards the crane by the spring J. The slide 51 has a piston-shaped end G2 for shutting off the oil flow from the second pressure channel A2. Within the scope of the invention, such an embodiment of the hydraulic motor is also possible where the shaft of the piston hydraulic motor is driven. Other hydraulic motor solutions are also possible. 10 15 20 25 30 532 733 12 In this application, duct is understood to mean pipes, hoses, bores and other similar connections. In this application, the term permit or drive permit or the partial or full-speed volume has been used in connection with certain cylinder groups and to these pistons in the fl recapacity engine. The rev volume can be full rev volume Val + Va; or partial speed Val.

FIG. 5 shows an embodiment of a pruning and cutting head M according to the invention in a forest felling machine, where the head comprises only one capacity capacitor 1 and only one ordinary piston / hydraulic cylinder group Val in this series-connected motor 3. In this embodiment the harvester head M can thus comprise only two a feed roller dl connected to the multi-capacity motor and a feed roller d; which is connected to the standard hydraulic motor 3. The rollers dl and d; can press the tree, for example, against a slippery abutment surface. The most advantageous form of dehydration, however, is that, for example, in FIG. 2A shows the discharge form, which is equipped with four hydraulic motors.

FIG. 6 shows illustratively radial cylinders and pistons in an engine according to the prior art. The embodiment shown in the figure has eight pistons and thus eight cylinders and the cylinder / piston group Val can thus comprise, for example, four pistons and more. these connected cylinders resp. the Va group; may comprise four pistons and cylinders.

FIG. 6 thus shows a cross section of a radial piston hydraulic motor with eight hydraulic cylinders and pistons connected to them.

In the Val + Va state; hydraulic oil with working pressure is led to all pistons in the working phase. In the Val condition, hydraulic oil with working pressure is led only to the group Val, while only hydraulic oil with low pressure, not oil with working pressure, is led in the condition in question to the pistons in the working phase in the Va phase; 532 'F33 '13 However, the pistons that are currently in the working phase with working pressure from the pump P1 can vary in the same hydraulic motor.

Claims (10)

10 15 20 25 30 532? 33 14 Patent claims Drive system (100) for hydraulic motors (1, 2,3,4) which drive tree feeder devices (d1, d2, d3, d4) in a pruning and cutting head (M) in a harvester, characterized in that - the drive system (100 ) comprises at least one fl capacity motor (1, 2) driving a feed roller (d1, d2) or equivalent and at least one second hydraulic motor (3,4) connected thereto driving a feed roller (d3, d4) or equivalent for feeding a tree , - the multi-capacity motor (1,2) in the system (100) being a radial piston hydraulic motor, comprising pistons (V) and on these pressure rollers (64), which are arranged to press against a cam ring (65) and which hydraulic motor (1,2 ) comprises a distributor (60) or a distribution valve, with which a pressurized medium, such as oil, can be phased to the piston malam cylinders (Va1, Va2), - with which drive system (100) can be selected for drive condition either a full speed volume (Va1 + Vaz) or a partial revolution volume (Va1), the motor connected to the multi-capacity hydraulic motor (1,2) parts (Va1, Va2), one of which is connected in series with the second hydraulic motor (3,4) in question and that the other of the motor parts (Vag) of the multi-capacity motor (1 or 2) can be connected to a pump (P1) in such a manner, that the second hydraulic motor (3,4) is bypassed with respect to the oil flow, and - that the drive system (100) comprises a control connection from the motor part (Va1) which realizes the sub-volume of the multi-capacity motor, from a pressure line (A1) therein, to a function means (50 ) which controls the drive state so that when the pressure in the part in question, in its pressure line (A1), falls below a certain pressure limit, the function means (50) closes the second motor part (Vaz) and the multi-capacity motor (1,2) is transferred to partial speed. System (100) according to claim 1, characterized in that the drive system (100) comprises at least two parallel fl capacitance motors (1,2), which drive the feed rollers (d1, d2) for feeding the tree and at least two other parallel ordinary hydraulic motors (3). , 4) comprising the feed rollers (d3, d4) or equivalent for feeding the tree. Ordinary hydraulic motors (3,4) comprising the feed rollers (d3, d4) or the like for feeding the tree. Drive system (100) according to claim 1 or 2, characterized in that the second hydraulic motor (3,4) in question is an ordinary motor, the speed of which can be regulated only by increasing or decreasing the pump feed. Drive system (100) according to one of the preceding claims, characterized in that the receptacle hydraulic motor (1,2) is a radial piston hydraulic motor comprising pistons (V) and on these pressure rollers (64) which are arranged to press against a cam ring ( 65) and which hydraulic motor (1, 2) comprises a distributor (60) or a distribution valve, with which a pressurized medium, such as oil, can be phased to the pistons / cylinders (Va1, Va2) and in which capacity motor (1,2) or in connection with this there is an arrangement in which the channel (A2) can be closed by displacing a slide (51) in a control valve (50), whereby the part (Vag) of the cylinders and the pistons can be brought into a so-called resting phase, wherein the pressurized medium can be conveyed only to said part (Ven) of the cylinders, whereby their speed of movement increases and the rotational speed of the hydraulic motor (1, 2) increases correspondingly, but the torque of the hydraulic motor (1,2) then decreases. Drive system (10) according to the preceding claim, characterized in that the system comprises such a multi-capacity motor (1,2) where there is a direct input from the pump (P1) to a motor part (Vag) therein. Drive system (100) according to one of the preceding claims, characterized in that the output of the recapacity motor (1,2) is connected to one of the outputs of the motor parts and that in the system a channel (11) coming from the pump is branched into two corresponding channel systems , of which one duct system (M1) is connected to one the other multi-capacity motor (2) and the second ordinary hydraulic motor (4) connected to it. Drive system (100) according to one of the preceding claims, characterized in that the system (100) comprises a pressure connection (C10) from the motor part (Va1) which realizes a sub-volume in the multi-capacity motor (1,2) to the controlling function means (50). and that when the pressure in the part in question, in its pressure line (A1), falls below a certain pressure limit, the operating means (50) closes the second motor part (Vaz) and the fl capacitance motor (1,2) is then transmitted to partial speed. Drive system (100) according to one of the preceding claims, characterized in that the feeding devices in the harvester head harvester head (M) are feed rollers (d1, d2, d3, d4) which can be connected to the surface of the tree to be fed for feeding it. . Drive system (100) according to one of the preceding claims, characterized in that the pressure and capacity of the pump (P1) in the normal operating situation are kept within a certain functional value range and that the rotational speed between the hydraulic motors (1, 2,3,4) in the system can then is regulated so that the ratio of the rotational speeds of the hydraulic motors (1, 2,3,4) to each other does not change at different rotational speeds when reversing the drive state of the fl recapacity motor (1,2), ie revolution volume from (Va1 + vag) to (Va1) or vice versa. Drive system according to Claim 1 or 2, characterized in that the functional means (50) consists of a slide (51) on which the pressure in the pressure line (A1) acts directly or indirectly and against the spring force of a spring (J) on the slide (51). , whereby when the pressure in the line (A1) drops below a certain limit, the slide (51) is displaced to a position where the second pressure line (A2) is closed. 533 733 17 i "fi íen (A1) sinks under a certain" '- grans forsk'ut rd ~ - - tfycklinien (A2) closes. J S s 'en (51) h "ett' age dar den andra