WO1985003983A1

WO1985003983A1 - Valve for adjustable, hydraulic driving means

Info

Publication number: WO1985003983A1
Application number: PCT/NO1985/000010
Authority: WO
Inventors: Botolv L. Larsen
Original assignee: Larsen Botolv L
Priority date: 1984-02-27
Filing date: 1985-02-26
Publication date: 1985-09-12
Also published as: NO157211C; NO157211B; EP0174332A1; NO840728L

Abstract

Valve for regulating a hydraulic driving means, comprising a hydraulic pump (1) which is adapted to the valve for transferring hydraulic fluid through the valve for operating a hydraulic motor (8, 9), the valve being regulated by means of control handles (21a, 22a) for setting the valve in various operating conditions of the driving means. For the purpose of providing a valve having excellent operating properties and compact bulk dimensions, there are, according to the invention, suggested two in the same valve housing (17) arranged valve members (21, 22), which can be operated independently of each other by a respective control handle (21a, resp. 22b), the valve members (21, 22) being arranged rotatable about a common axis in either half of the housing (17). The two valve members (21, 22) can be connected to a common oil pressure chamber (5) which communicates with the hydraulic pump (1), and each valve member (21, 22) is provided with a plurality of corresponding groups of oil channels (A1 to A4, A11 to A14 resp. B1 to B4, B11 to B14), which can be connected to respective hydraulic conduits (10, 11 resp. 12, 13) for operating respective hydraulic motors (8 resp. 9) in various independent rotational directions and with various independent speeds.

Description

Valve for adjustable, hydraulic driving means

The present invention relates to a valve for an adjust¬ able, hydraulic driving means for one or more hydraulic motors, which are used for the operation of machines, basket lifts or trolley carriages for transport on supporting rail or cable railway.

More specificly, the invention relates to a valve for an adjustable, hydraulic driving means, comprising a hydraulic pump which is adapted to the valve for transferring hydraulic fluid through the valve for driving a hydraulic motor, as well as control handle for setting the valve for various working conditions of the driving means, said valve comprising two valve members which are provided in the same housing and which can be operated independently by a respective control handle, said valve members being arranged in either half of the housing for rotation about a common axis.

From NO patent specification 92 862 there is known a. . driving means which is particularly applicable for operation of trolley carriages for rail- or cable-crane, in which the trolley carriage is influenced in opposite direction by two lines having winches connected to respective driving means. The means comprises four fluid motors as well as two separate valves having a respective control handle, two of the fluid motors being connected to one of the winches, whereas a third fluid motor is connected to the second winch, and the three fluid motors being driven by a volumetric pump which is con¬ nected to a mechanical driving source.

From US patent specification 3 026 905 there is known a multiple valve which is composed of four series connected valve housings. Compressed air is supplied at the one end of the valve and is via a through-going bore distributed to the various valve members for effecting the various functions. These functions can for example be the supply of air for engaging and disengaging a drill guide, the control of flushing water to a rock drill, etc. The individual valve members are adapted for being connected to various drive means, and they do not comprise a plurality of corresponding groups of hydraulic channels which can be connected to respec¬ tive hydraulic driving conduits for operating one or more hydraulic motors associated with each valve member in various independent directions.

From US patent specification 2 450 625 there is known a hydraulic control valve for controlling a stream of fluid through the valve, the control valve comprising a wheel-like rotor having a plurality of channels of various sizes. This known valve is intended for use for driving a motor in one direction only, i.e. various rotational directions for the motor cannot be achieved with the known control valve, because it is not adapted for being connected to several hydraulic conduits.

The object of the present invention is to provide a valve for an adjustable, hydraulic driving means, which renders a compact construction, the number of hydraulic motors or fluid motors and their speed and rotational directions being variable within wide limits.

The object is achieved in accordance with the invention by a valve of the type given in the preamble, which according to the invention is characterized in that the two valve members are constructed such that they form a common oil pressure chamber which is in communication with the hydraulic pump, each valve member being provided with a plurality of corre¬ sponding groups of oil channels which can be connected to respective hydraulic conduits for operating one or more hydrau¬ lic motors associated with each valve member in various inde¬ pendent directions of rotation.

The two valve members have an axial extension along their common rotational axis which is larger than the distance between corresponding oil conduits, a fact which involves that the individual valve member including its oil channels can come into registry with the hydraulic conduits. A first couple of groups of oil channels communicate with the oil pressure chamber, whereas another couple of groups are connec¬ ted to the oil pit, and by turning the control handle in various directions, one can achieve various rotational speeds of the associated hydraulic motor, as well as alter the rotational direction thereof.

In the following the invention will be further discussed, reference being had to the drawing which illustrates an example of an adjustable hydraulic driving means, in which an embodi¬ ment of the present valve is included.

Figure 1 is a schematic side view of a cable railway in which a driving means with the valve according to the present invention can be included.

Figure 2 is a schematic view, partly in section, of an embodiment of a valve for a hydraulic driving means, the valve here being illustrated in a first operating position.

Figure 3 illustrates schematically a first control handle for controlling a member of the valve.

Figure 4 is a schematic view similar to Figure 2, another operating position of the valve being illustrated therein.

Figure 5 is a schematic view of another control handle for the valve.

Figure 6 is a view similar to Figures 2 and 4 and illu¬ strates a third operating position of the valve.

Figure 7 is a fraction of the right side of the valve in a given operating position.

Figures 8a and 8b are a view as seen from above of the valve and a view as seen from below of the valve, respec¬ tively.

Figure 9 is another embodiment of the valve, in which it is connected to four hydraulic motors.

In Figure 1 there is shown a cable railway in which a driving means comprising a valve according to the invention may be applicable. The Figure illustrates a cable railway, in which a supporting cable 130 extends between the first end attachment A of the cable railway and the second end attachment B thereof, at which a double caster tightening pulley 122 is provided. As it appears from Figure 1, the cable railway comprises a first operating line 110, extending from a first winch 101 over a caster 113 and further towards a trolley carriage 120, the line 110 here running over a caster 114 and around a pulley caster 115 for a loading hook 131 for thereafter being attached to the underside of the trolley carriage 120.

Such a guiding of the line 110 involves that the loading hook 115 is operated by the line 110, since it during tighten¬ ing of said line will be pulled up towards the trolley carriage 120 and be attached thereto during the transportation of load on the cable railway.

Further, it is in Figure 1 illustrated a second operating line 111 extending from a second winch 102 over a double caster 116 provided on the frame attachment A of the cable railway. From here the line 111 extends to a pulley 118 at the second end attachment B of the cable railway, after first having been passed through the trolley carriage 120 below a caster 126 at each side of the trolley carriage 120. At the end attachment B of the cable railway the line 111 is passed around the one caster of the pulley 118 for being returned to the trolley carriage 120, where it is attached to the left side thereof, as it appears from Figure 1.

In Figure 1 there is also depicted a further line 125 which is attached to the left side of the trolley carriage 120, the line 125 here extending parallelly to the line 111 over a second caster in the pulley 118 and further back towards the trolley carriage 120 parallel to the line 111, also here via a caster 126 on each side of the trolley carriage 120. Further, the line 125 is passed over the double caster 116, but is returned herefro for being attached to the right side of the trolley carriage 120.

Thus, in the illustrated arrangement the line 125 con¬ stitutes together with the line 111 and partly the line 110, respectively, whilst the trolley carriage 120 constitutes a connection between the said lines, a double carrying line for the trolley carriage 120 between the double caster 116 at the end attachment A of the cable railway and the pulley 118 at the end attachment B of the cable railway. The above discussed pulley 118 which carries the double line 125, 111, is affixed to the end attachment B of the cable railway by means of a pulley means comprising two double- casters, here pulley 119 and 121 which are mounted at the end attachment B of the cable railway, there being used two tensioning lines 128 and 129, respectively, having equal length and being guided over their own caster in pulley 119 and pulley 121, respectively. Together with the pulley 122 of the supporting line the tensioning lines 128 and 129 are affixed as illustrated in the Figure.

In the illustrated arrangement the supporting line 130 can be tightened by loading, and it is presumed that for the field railway there is used a steel cable of known type having a holding power of for example 250.000 kg for the supporting line 130. For the line 125 there can be used a

2 soft wire having for example a sectional area of 2 cm and a holding power of for example 40.000 kg.

For the lines 110 and 111 there can be used soft wires having holding power of approx. 25.000 kg.

Finally, for the tensioning lines 128 and 129 there can be used soft wires of known type having a holding power of 50.000 kg.

The tensioning of the supporting lines of the cable railway illustrated in Figure 1 , is realized in that the trolley carriage 120 constitutes a connection for the double line 125, 111 and 110, respectively, which are moved around a caster in the pulley 116 and a caster in the pulley 118 when the trolley carriage 120 by means of the operating line 110 is pulled towards right, or when the line 111 is pulled towards left, on the supporting lines of the cable railway.

In the here chosen example there is between the pulley 116 and the pulley 118 transferred a tensioning power of 80.000 kg distributed on the two parts of the line 125. In addition there exists a hydraulic pulling force on the pulley 118 towards left from the line 110 and line 111 when the trolley carriage 120 of the cable railway is driven towards right or towards left on the supporting lines. On the pulley 118 one can in this connection obtain a hydraulic line stretch totalling 24.000 kg. Together with the tensioning force of 80.000 kg along the line 125 the pulley 118 can here obtain a line tensioning of 100.000 kg. In Figure 1 it appears ^*hat this line tensioning is transferred via a pulley device which here is used to keep the supporting line of the cable railway tensioned as required, for example up to 200.000 kg. It is to be noted that since the double line 125 and 110, respec¬ tively 111 serve as supporting lines for the trolley carriage 120 of the cable railway between the end attachment A and B of the cable railway, the trolley carriage of the cable railway can be driven with a total line stretch of approx. 300.000 kg.

The winches 101 and 102 are driven via a hydraulic means which will be further discussed in the following, reference being had to the other Figures.

Thus, it is in Figures 2 to 8 illustrated a hydraulic driving means for operating a trolley carriage along a cable railway of the type illustrated in Figure 1. The cable railway can for example be driven with 120 horse powers at the same time as the supporting line of the cable railway is tightened upon loading.

In Figure 2, which diagrammatically illustrates a view, partly in section, of an embodiment of a valve according to the invention connected to a hydraulic driving means, 1 designates an oil pump which can be driven by for example a combustion engine, for example a car engine or a tractor engine or similar, connected to the shaft 2 of the oil pump 1. The oil pump 1 is connected to a pit 6 by means of a conduit 3 and is also by means of a second conduit 4, i.e. a pressure conduit, connected to an oil pressure chamber 5 which is formed by two rotatable valve members, here designated valve members 21 and 22, which are provided with their own control handle, 21a and 22a, respectively. The two valve members 21 and 22 are provided in either half of a cylinder-shaped valve housing 17, the valve housing 17 being adapted for through a channel 4a to receive the oil pressure conduit 4 at its center portion, and in this area also being provided with an over-pressure valve 7 connected in a channel 4b between the two valve members 21 and 22 in an area in which the latters form the pressure chamber 5..

By relating Figure 2 and Figures 8a and 8b to each other, it is seen that to the upper side of the valve housing 17 there are connected four oil conduits 10, 11, 12, and 13, the oil conduit 10 and the oil conduit 11 being connected for communication with the left valve member 21, and the same oil conduits 10 and 11 being connected to a fluid motor 8 which in turn via a gear transmission 16 -is connected to the above-mentioned winch 101 illustrated in Figure 1. Further, two oil conduits 12 and 13 are arranged for communication through the valve housing 17 with the right valve member 22 and with another fluid motor 9 which in turn via a gear transmission 16 drives the second winch 102 which is discussed in connection with Figure 1.

Thus, the two valve members 21 and 22 can be operated independently of each^' other by means of their own control handle 21a and 22b, respectively, the mentioned valve members being provided rotatable- about a common axis in each half of the valve housing 17. The two valve members 21 and 22 have an axial extension which is larger than the distance between the associated oil conduits, i.e. the valve member 21 has a longer axial extension than the distance between the oil conduits 10 and 11, whereas the valve member 22. has an axial extension exceeding the distance between the conduits 12 and 13.

The common pressure chamber 5 is partly defined by sub¬ stantially cylindrical axial recesses 5a and 5b, respectively, in each of the two valve members 21 and 22, respectively, the recesses 5a, 5b with their orifices 5x, 5y abutting against either side of a central inwardly protruding valve housing wall -portion 17a comprising the channel 4a connected to the above-mentioned conduit 4 from the hydraulic pump 1 , as well as the second channel 4b having the overpressure valve 7 provided therein. Each valve member 21, 22 is, as it appears especially from Figures 3 and 5, equipped with a plurality of oil channels extending from the cylindrical surface of the valve member and to the orifice, 5a and 5b, respectively, defining the pressure chamber 5. Thus, each of the valve members 21 and 22 comprises two sets of oil channels, which are arranged in pairs, a first set being designated by A1 , A2, A3, A4, and the second set being designated by B1 , B2, B3, B4. As seen in the longitudinal direction of the valve member, the four first-mentioned oil channels A1 to A4 are arranged in the left half of the valve member 21, 22_r respectively, whereas the four other oil channels B1 to B4 are arranged in the right side of the respective valve members. This involves that in dependence of whether the individual valve member 21 or 22 is rotated in the one or the other direction by means of its control handle 21a or 22a, respectively,, either the oil channels or the oil orifices A1 to A4 will arrive at a position which mutually registers with the left hydraulic conduit 10 or the conduit 12, whereas a rotation in the oppo¬ site direction will bring the oil channels or oil orifices B1 to B4 in register with the oil conduit 11 or oil conduit 13, respectively, depending on which valve member is to be rotated. Thus, a rotation in one or the other direction of the valve members will involve that the fluid motors 8 and 9, respectively, will rotate in different direction.

Depending on the sectional area of the above-mentioned channels or oil orifices A1 to A4, B1 to B4, respectively, it is possible not only to achieve various rotational di¬ rections of the fluid motors 8 and 9, respectively, but also different rotational speeds, since in the illustrated embodi¬ ment it is possible to have the same sectional area for the

2 oil channels Al and B1 , for example 2 cm , whereas the oil orifices A2 and B2 can be provided with a sectional area of

2 for example 1,5 cm . The oil orifices A3 and B3 can for example

2 hav e sectional area corresponding to 1 cm , whereas the oil orifices A4 and B4 may have a sectional area corresponding

2 to 0,5 cm . It is thus to be understood that the above-mentioned set of oil orifices or oil channels A2 to A4 and B1 to B4 which are shaped in the same manner for the two valve members 21 and 22, respectively, can be connected to the above- mentioned pressure chamber 5, and for each oil channel or oil orifice there are at at axial distance corresponding to the distance between the said oil conduits 10 and 11, respec¬ tively 12 and 13, provided return channels which in turn via a bypass recess 18a or 18b in the respective valve half 21 or 22 return the oil to the pit 6. These return channels are appropriately designated by A11 to A14,.B11 to B14, respec¬ tively.

The function of the above discussed valve for regulating one of the hydraulic driving means, especially for operating a cable railway as discussed in connection with Figure 1 , will in the following be further described.

As it appears from Figures 2, 3 and 6, the rotatable valve half 21 is regulated by means of the control handle 21a. If the control handle 21a is in a center position as illustrated to the left of Figure 6, all of the oil flow between the oil chamber 5 of the valve and the fluid motor 8 will be blocked. This involves that with the control handle 21a in a central position or in a position right up or right down, the motor 8 and the associated winch 101 and the line 110 of the cable railway will be in a hydraulically locked position.

To the left of Figures 2 and 4 there is illustrated the rotatable valve 21 in a position which allows a driving oil flow to come from the oil pressure chamber 5 of the valve via the oil conduit 10 in Figure 2 or via the oil conduit 11 in Figure 4, the rotation of the control handle 21a in the first or the second direction making it possible to select the rotational direction of the fluid motor 8 driving the winch 101 for tightening or slackening the line 110 of the cable railway.

To the left of Figure 2 the oil orifice A1 and the. return channel A11 in the valve member 21 is depicted with a largest cross-sectional area, whereas in Figure 4 the oil orifice B3 and the return channel B13 are depicted with a reduced sectional area corresponding to another rotational speed of the fluid motor 8 in the one or the other direction.

To the right of Figures 2 and 4 the rotatable valve 22 is depicted in various operational positions which allow either a less oil flow to pass from the oil chamber 5 of the valve to the oil conduit 15 (Figure 2) or a larger oil flow to be supplied to the oil conduit 13 (Figure 4), the rotation of the control handle 22a in either the first or the second direction allowing for various speed and rotational direction for the fluid motor 9 driving the winch 102 for tightening or slackening the line 111 of the cable railway.

As it appears from Figure 5, the rotatable valve member 22 is regulated by means of the control handle 22a. If the control handle 22a is in a central position or right upwardly as it is illustrated for the control handle 21a to the left in Figure 6, the complete oil flow between the oil pressure chamber 5 of the valve and the fluid motor 9 will be blocked,

» and the motor 9 with the associated winch 102 as well as the associated cable railway line 111 will then be hydrauli- cally locked.

In the position which is illustrated in Figure 2„ the control handle 21a of the valve 21 can take a slanted position to the right relative to the central position, for example of 25 , which corresponds to the oil orifice A1 in the valve

21 registering with the conduit 10 and transferring a driving

2 oil flow of 2 cm to the fluid motor 8 which then drives the winch 101 for tightening the line 110 of the cable railway.

The control handle 22a for valve 22 is in Figure 2 rotated to a slanted position towards right to define an angle of for example 50 , which involves that the oil orifice A3 in

2 the valve 22 conducts a driving oil flow of only 1 cm through the conduit 12 to the motor 9, which in turn drives the winch

102 for tightening the line 111 of the cable railway. On its way back to the pit 6 the oil will pass the return channel

A13 and the circumferential recess 18b. With the same construction of the driving means for the winch 101 and the winch 102 it is appropriate to provide the same with a hydraulic or mechanical gear for tightening the line 110 of the cable railway on the winch 101 and the line 111 of the cable railway on the winch 102 with an initial speed of for example 25 cm/second. If a lifting speed of 25 cm/second is used, it is possible with 120 horse power available to achieve a tightening force on the lines 110 and 111 totalling 36.000 kg.

It is presumed that the trolley carriage 120 has been driven to a selected position on the cable railway for picking up a load. At this position the trolley carriage is stopped by putting both the valve handle 21a and the valve handle 22a to their central position. The valve handle 21a is there¬ after brought 25° from its central position towards left, i.e. so that the oil orifice B1 in the valve 21 becomes con¬ nected to the oil conduit 11 for the fluid motor 8. The line 110 will then be hauled off from the winch 101, which includes that the loading pulley 115 of the trolley carriage is lowered.

When the load hook 131 has reached a desired position on the ground, the control handle 21a is pulled back to its central position, involving that the line 110 will be held steady for loading. The pulley 115 can for example be loaded with 1200 kg.

Thereafter, the valve handle 21a is moved 25° towards right from its central position, involving that the oil orifice A1 in valve 21 will be connected to the oil conduit 10 for the fluid motor 8, and the line 110 will then be tightened onto the winch 101 and the load simultaneously lifted to the trolley carriage 120.

When the load is lifted to the trolley carriage and is to be driven towards right on the supporting lines of the cable railway, the control handle 22a of the valve member -22 is moved from its central position 25° towards right, which involves that the oil orifice A1 of the valve member 22 is connected to the oil conduit 12 for the fluid motor 9 for tightening the line 111 onto the winch 102. The valve handle 21a is thereafter moved 50 towards right from its central position for thereby connecting the oil orifice A3 of the valve member 21 to the oil conduit 10 for the fluid motor 8 for tightening the line 110 onto the winch 101.

The 120 horse powers which are available for the hydraulic driving means will in this position of the control handles 21a and 22a be distributed in the oil pressure chamber 5 giving 80 horse powers for the fluid motor 9 driving the winch 102 and 40 horse powers for the fluid motor 8 driving the winch 101.

In the chosen example the line 110 is reeled onto the winch 101 with a force of 12.000 kg, whereas the line 111 is reeled onto the winch 102 with a force of 24.000 kg. This power situation involves that the trolley carriage with load can be driven in the direction towards left on the supporting lines of the cable railway.

In other words, the trolley carriage 120 can be pulled towards left by hauling the line 111 onto the winch 102, whereas it can be pulled towards right when the line 110 is reeled onto the winch 101.

In Figure 2, which illustrates the oil orifice A1 in the rotatable valve member 21 connected to the oil conduit 10, which here drives the fluid motor 8 with two third of the oil flow from the pressure chamber 5 of the valve, the line 110 is reeled onto the winch 101 with a force of 24.000 kg.

Figure 2 illustrates correspondingly that the oil orifice A3 in the rotatable valve member 22 is connected to the oil conduit 12 driving the fluid motor 9 with a third of the oil flow from the valve pressure chamber 5. The line 111 is then reeled onto the winch 102 with a force of 12.000 kg. This power situation allows for a driving direction towards right.

To the right in Figure 6 there is illustrated a position of the valve member 22 corresponding to the position A4 or B4 in Figure 5, a position which involves that the oil conduits 12 and 13 communicate directly without going through the pressure chamber 5 in the valve. Such a position includes an idle position or free position of the corresponding fluid - motor which drives the winch 102, a fact which is favourable under certain operating conditions.

It is to be understood that also the valve 21 can be provided with corresponding idle or free positions, which may be favourable during the lowering of the load on the hook 131.

In Figure 7 there is illustrated on a larger scale a fraction of the right side of the valve in a given operating position, i.e. an operating position corresponding to the handle 22a being rotated 25° from its zero position towards right, a fact which involves that the valve chamber A1 will communicate with the oil conduit 12 driving the fluid motor 9, and it is thereby achieved the same operating conditions for the motor 9 as illustrated to the right in Figure 4, but with opposite rotational direction. In Figure 7 the return channel A11 is connected on the one hand to the oil conduit 13 and on the other hand to the circumferential recess 18b which in turn communicates with the pit.

It is to be understood that the oil channels A1 to A4 and B1 to B4 which are illustrated in Figure 3 and Figure 5, not necessarily must be located in the sequence illustrated in said Figures.

Since there between each oil channel is provided a portion of'goods which closes the inlet and outlet associated with the respective couple of oil conduits 10 and 11 for valve members 21 and 12 and 13 for valve member 22, respec¬ tively, it is also possible to arrange the oil channels alter¬ nating, i.e. in the sequence A1 , B1 , A2, B2, A3, B3 for the one set of oil channels and B1 * , A1 * , B2', A2', B3' , A3' for the other set of oil channels of the same valve member. This involves that by turning the control handle in one and the same direction one will first arrive at the oil channel A1 which renders a motor rotation in the first direction. By a futher turning of the control handle in the same direction one will come into an idle zone between A1 and B1 , where¬ after a further turning of the control handle will connect the oil channel B1 and thereby render a motor rotation in opposite rotational direction.

Correspondingly, it is possible by turning the control handle in opposite direction to pass the other set of oil channels, i.e. firstly the channel Bl ' giving a rotation of the motor in a first direction, then an idle zone between the channel B1 ' and Al', whereafter one arrives the zone for channel Al ' giving a rotation of the motor which is in opposite direction, etc.

It is to be understood that the valve according to the present invention can also be used for operating more hydraulic motors than one, there being provided for each valve member a plurality of groups of hydraulic driving conduits which in turn can be connected to one or more hydraulic motors. These can in turn be-connected to the hydraulic driving conduits in such a manner that the various positions of the corre¬ sponding valve member will give various rotational directions and power for thereby achieving a still finer regulation of the torques which are to be transferred to the shaft to which the hydraulic motors are connected.

Such a device is illustrated in Figure 9, Figure 9 being a diagrammatical view, partly in section, through a valve which is connected to four hydraulic motors.

In Figure 9 the parts which are previously discussed, are designated by reference numbers to which is added 200, whereas the members which have been added have been given an appendix x.

It is to be understood that in Figure 9 there has been chosen an arbitrary position of the valve members 221 and 222, respectively, the various channels A101, A111 etc. being provided with various cross-sections, so that the hydraulic motors 208 and 208x, 209 and 209x, respectively, which are connected in pairs, can obtain different rotational directions and speeds.

Claims

P a t e n t C l a i m s

1. Valve for an adjustable, hydraulic means, comprising a hydraulic pump (1) which is adapted to the valve for trans¬ ferring hydraulic fluid through the valve for driving a hydraulic motor (8, 9), as well as a control handle (21a, 22a) for setting the valve for various working conditions of the driving means, said valve comprising two valve members (21, 22) which are provided in the same housing (17) and which can be operated independently by a respective control handle (21a, 22b respectively), said valve members (21, 22) being arranged in either half of the housing (17) for rotation about a common axis, c h a r a c t e r i z e d i n that the two valve members (21, 22) have a common oil pressure chamber (5) which is connected to the hydraulic pump (1), and that each valve member is provided with a plurality of corresponding groups of oil channels (A1 to A4, B1 to B4), which can be connected to respective hydraulic driving conduits (10, 11 resp. 12, 13) for operating a hydraulic motor (8 resp. 9) associated with each valve member in various indepen¬ dent directions.

2. Valve as claimed in claim 1, c h a r a c t e r i z e d i n that the oil channels in each group have different sectional area for permitting different throughput of oil and thereby different rotational speed of the corresponding fluid motor (8 resp. 9).

3. Valve as claimed in claim 1 or 2, c h a r a c t e ¬ r i z e d i n that each oil channel in a group (A1 to

A4 resp. B1 to B4) is adapted to connect the associated fluid motor (8 resp. 9) to the valve pressure chamber (5), and that to each oil channel or oil orifice (A1 to A4 resp. B1 to B4) there is provided an axially offset return channel (A11 to A14 resp. B11 to B14) communicating with the oil • pit (6).

4. Valve as claimed in any of the claims 1 to 3, c h a r a c t e r i z e d i n that each of the two valve members (21, 22) has an axial extension which is larger than the distance between corresponding oil conduits (10,

11 resp. 12, 13) which connect the pressure chamber (5) to the fluid motors (8 resp. 9).

5. Valve as claimed in any of the claims 1 to 4, c h a r ac t e r i z e d i n that the common pressure chamber (5) for the two aligned valve members (21, 22) is constituted by primarily cylindrical axial -recesses (5a, 5b) which with their orifices (5x, 5y) abut against each side of a central, inwardly protruding valve housing wall section (17a) comprising a channel (4a) connected to the conduit (4) for the hydraulic pump, as well as a channel (4b) in which is provided a safety valve (7).

6. Valve as claimed in any of the claims 1 to 5, c h a r a c t e r i z e d i n that in each valve member (21, 22) there is defined a circumferential track (18a, 18b) in the area between the connection points (A1 to A4, A11 to A14) of the oil conduits (10, 11) of the fluid motors, the circumferential track (18a, 18b) serving to return oil under pressure back to the pit (6) provided at the underside of the valve housing (17).

7. Valve as claimed in any of the claims 1 to 3, c h a r a c t e r i z e d i n that the groups of oil channels which can communicate with respective hydraulic driving conduits (10, 11 resp. 12, 13) are arranged in a sequence (A1 , B1 , A2, B2, A3, B3) which alternating renders different rotational direction of the associated hydraulic motor (8 resp. 9) if the valve member (21 resp. 22) by means of the handle (21a resp. 22a) is moved in one and the same direction.