The present invention relates to a hydraulic crane according to the preamble of claim 1 . A hydraulic crane, for instance in the form of a lorry crane or forestry crane, normally comprises a column , which is rotatable about a vertical axis of rotation , and a crane boom system, which is mounted to the column and which is intended to carry a load in a load suspension point at an outer end of the crane boom system , wherein the crane boom system comprises two or more liftable and lowerable crane booms which form a connection between the load suspension point and the column and which are articulately connected to each other. The crane also comprises a manoeuvring unit with one or more maneuvering members configured to be manoeuvrable by a crane operator in order to control the crane boom movements. I n order to facilitate for the operator to control the position of the load suspension point in an accurate manner, the control of the crane boom movements is with advantage based on so-called boom tip control . I n the case of boom tip control , a first maneuvering member may be used for controlling the rotation of the col umn, a second maneuvering member may be used for controlling the movement of the load suspension poi nt in a vertical direction in order to control the height of the load suspension point and a third maneuvering member may be used for controlling the movement of the load suspension point i n a horizontal direction in order to control the lifting radi us. The manoeuvring unit could as an alternative be provided with a maneuvering member i n the form of a joystick to be used for controlling the movement of the load suspension point i n the vertical and horizontal directions. In connection with boom tip control , the individual movements of the crane booms of the crane boom system are regulated by an electronic control device based on control signals from the manoeuvring unit and a calculation model for boom tip control , wherein the calculation model is established by the crane manufacturer in accordance with a given control strategy. Thus, when boom tip control is used , the crane operator has no direct control over the positioning of the i ndividual crane booms. On the contrary, the electronic control device calculates how the individual crane booms should be moved i n order to make the load suspension point follow the trajectory specified by the crane operator via the manoeuvring unit.

The load suspension poi nt of an ordinary lorry crane may be provided at the outer end of a crane boom in the form of a so- called outer boom, which is telescopically extensible and articulately connected to another crane boom in the form of a so-called inner boom, wherei n the inner boom in its turn is articulately connected to the rotatable column of the crane. When a crane operator controls such a crane based on boom tip control , the crane operator normally has his attention directed to the load suspension poi nt at the outer end of the outer boom and is not always aware of the prevailing position and the coming movements of the inner boom, which implies that there is a risk for the inner boom to collide with the driver's cab of the lorry or any other obstacle within the working area of the crane.

OBJ ECT OF THE I NVENTION

The object of the present invention is to provide a sol ution to the above-mentioned problem.

SUMMARY OF THE I NVENTION

Accordi ng to the present i nvention , said object is achieved by means of a hydraulic crane having the features defined in claim 1 .

The hydraulic crane accordi ng to the present invention comprises:

- a crane base;

- a col umn which is rotatably mounted to the crane base so as to be rotatable in relation to the crane base about an essentially vertical axis of rotation ;

- an actuating device for rotating the column in relation to the crane base;

- a crane boom system comprising two or more liftable and lowerable crane booms which are articulately connected to each other and hydraulic cylinders for lifting and lowering the crane booms, wherein a first crane boom of the crane boom system is articulately connected to the column and a second crane boom of the crane boom system is articulately connected to the first crane boom;

- an electronic control device for controlling said actuating device and the hydraulic cylinders of the crane boom system to thereby control the rotation of the column and the positioning of the crane booms; and

- a manoeuvring unit with one or more maneuvering members configured to be manoeuvrable by a crane operator in order to control the position of a load suspension point of the crane boom system, wherein the manoeuvring unit is configured to supply the electronic control device with control signals related to the manoeuvring of said one or more maneuvering members. The electronic control device is configured to control the crane boom movements on the basis of said control signals and a calculation model for boom tip control , wherein the electronic control device in a first control mode is configured to make the load suspension point move along a trajectory defined by said control signals while controlling the crane boom movements in accordance with an ordi nary control strategy. The electronic control device is configured to switch from the first control mode into a second control mode when it is established by the electronic control device that the first crane boom is about to interfere with a predefined safety zone associated with a known obstacle or about to interfere with an obstacle detected by means of one or more sensors of the hydraulic crane, wherein the electronic control device in this second control mode is configured to make the load suspension poi nt move along said trajectory while controlling the crane boom movements in accordance with an auxiliary control strategy in which the first crane boom is prevented from interfering with the safety zone or the detected obstacle. Hereby, the first crane boom is automatically prevented from colliding with the obstacle without affecting the desired movement of the load suspension point ordered by the crane operator, and the crane operator may thereby keep his attention directed to the load suspension point at the outer end of the crane boom system without jeopardizing the safety of the crane.

Further advantages as well as advantageous features of the hydraulic crane according to the i nvention will appear from the following description and the dependent claims.

BRI EF DESCRI PTI ON OF TH E DRAWI NGS

The i nvention will in the following be more closely described by means of embodiment examples, with reference to the appended drawings. In the drawings:

Fig 1 is a schematic rear view of a lorry provided with a hydraulic crane according to an embodiment of the present invention,

Fig 2 is a schematic perspective view of a manoeuvring unit with a number of manoeuvring members for controlling different crane functions, is an outline diagram of the crane of Fig 1 , as seen in a lateral view with the load suspension poi nt of the crane i n a first position , is an outline diagram of the crane of Fig 1 , as seen in a planar view from above with the load suspension point of the crane in said first position , is an outline diagram of the crane of Fig 1 , as seen in a lateral view corresponding to Fig 3a and with the load suspension point of the crane in a second position , is an outline diagram of the crane of Fig 1 , as seen in a planar view corresponding to Fig 3b and with the load suspension poi nt of the crane in said second position , is an outline diagram of the crane of Fig 1 , as seen in a lateral view corresponding to Fig 3a and with the load suspension point of the crane in a third position , is an outline diagram of the crane of Fig 1 , as seen in a planar view corresponding to Fig 3b and with the load suspension poi nt of the crane in said third position , and is a schematic illustration of a hydraulic accordi ng to an embodiment of the invention . DETAI LED DESCRI PTI ON OF EMBODI MENTS OF THE I NVENTION In this description, the expression "liftable and lowerable crane boom" refers to a crane boom which can be pivoted i n a vertical plane so as to thereby perform liftings and lowerings of a load carried by the crane. The expression "hydraulic cylinder for lifting and lowering the crane boom" here refers to the hydraulic cylinder which is associated with the liftable and lowerable crane boom and which carries out the pivoting thereof in a vertical plane.

Fig 1 shows a hydraulic crane 1 mounted on a frame 2, which i n the illustrated embodiment is connected to the chassis 3 of a lorry 4. The frame 2 is provided with adjustable support legs 5 for supporting the crane 1 .

The crane 1 comprises:

- a crane base 6, which is fixed to the frame 2;

- a column 7, which is rotatably mounted to the crane base 6 so as to be rotatable in relation to the crane base about an essentially vertical axis of rotation A1 by means of an actuating device 8;

- a liftable and lowerable first crane boom 1 1 , here denominated inner boom, which is articulately connected to the col umn 7 in such a manner that it is pivotable in relation to the column about an essentially horizontal axis of rotation A2 ; - a first hydraulic cylinder 12, here denominated lifting cylinder, for lifting and lowering the inner boom 1 1 in relation to the column 7;

- a liftable and lowerable second crane boom 13, here denomi nated outer boom, which is articulately connected to the inner boom 1 1 in such a manner that it is pivotable in relation to the inner boom about an essentially horizontal axis of rotation A3; and

- a second hydraulic cylinder 14, here denominated outer boom cylinder, for lifting and lowering of the outer boom 13 i n relation to the i nner boom 1 1 .

In the illustrated example, the lifting cylinder 12 comprises a cylinder part 12a which is articulately connected to the column 7, and a piston which is received in the cylinder part 1 2a and displaceable in relation to it, wherein the piston is fixed to a piston rod 12b which is articulately connected to the inner boom 1 1 . The outer boom cylinder 14 comprises a cylinder part 14a which is articulately connected to the inner boom 1 1 , and a piston which is received in the cylinder part 14a and displaceable in relation to it, wherein the piston is fixed a piston rod 14b which is articulately connected to the outer boom 1 3.

In the illustrated embodiment, the crane boom system 10 of the crane 1 is formed by the inner boom 1 1 and the outer boom 1 3 and the associated hydraulic cylinders. However, the crane boom system 10 of the crane 1 may also include more than two liftable and lowerable crane booms articulately connected to each other. As an example, a liftable and lowerable crane boom in the form of a so-called jib may be mounted to the outer end of the outer boom 13 to thereby make it possible to perform lifting operations requiring a greater range. The outer boom 13 is telescopically extensible to enable an adjustment of the extension length L thereof. I n the illustrated example, the outer boom 13 comprises one telescopic crane boom section 1 3b, which is slidably received in a base section 13a of the outer boom 13 and displaceable in the longitudinal direction of the base section 13a for adjustment of the extension length L of the outer boom 13. The telescopic crane boom section 13b is displaceable in relation to the base section 1 3a by means of a hydraulic cylinder 1 5 carried by the outer boom 13. I n the illustrated example, this hydraulic cylinder 1 5 comprises a cylinder part 15a which is fixed to the base section 13a, and a piston which is received in the cylinder part 1 5a and displaceable in relation to it, wherein the piston is fixed to a piston rod 15b which is fixed to the telescopic crane boom section 13b. As an alternative, the outer boom 13 could comprise two or more telescopic crane boom sections 13b which are mutually slidable in relation to each other i n the longitudinal direction of the outer boom 1 3 for adjustment of the extension length thereof. In the illustrated embodiment, a rotator 16 is articulately fastened to a load suspension poi nt P at the outer end of the outer boom 13, which rotator in its turn carries a lifting hook 1 7. In this case, the load to be carried by the crane 1 is fixed to the lifting hook 1 7, for i nstance by means of lifting wires or the similar.

The control system for controlling the hydraulic cylinders 12, 14, 15 of the crane boom system 10 comprises a pump 20 (see Fig 6) which pumps hydraulic fluid from a reservoir 21 to a directional-control-valve block 22. The directional-control-valve block 22 comprises a directional-control-valve section 23 for each of the hydraulic cylinders 12, 14 and 15 of the crane boom system 1 0, to which hydraulic cylinders hydraulic fluid is supplied in a conventional manner in dependence on the setting position of the slide member in the respective directional- control-valve section 23. The crane 1 comprises a manoeuvring unit 24 (see Fig 2) with one or more maneuvering members S 1 -S3 configured to be manoeuvrable by a crane operator in order to control the position of the load suspension point P of the crane boom system 10. Control signals are transmitted via cable or a wireless connection from the manoeuvring unit 24 to an electronic control device 25, for instance in the form of a microprocessor, which in its turn controls the setting position of the slide members in the valve sections 23 of the directional- control-valve block 22 in dependence on control signals from the manoeuvring unit 24 related to the manoeuvring of the maneuvering members S 1 -S3.

The electronic control device 25 is configured to control the crane boom movements on the basis of the control signals from the manoeuvring unit 24 and a calculation model for boom tip control . The calculation model may for instance be stored as an algorithm in a memory of the electronic control device 25. A first maneuvering member S 1 may be used for controlling the rotation of the column 7 in relation to the crane base 6 about the vertical axis of rotation A1 , a second maneuvering member S2 may be used for controlling the movement of the load suspension poi nt P in a vertical direction in order to control the height of the load suspension point P and a third maneuvering member S3 may be used for controlling the movement of the load suspension poi nt P in a horizontal direction i n order to control the lifting radius, i .e. the horizontal distance between the load suspension point P and the vertical axis of rotation A1 . The manoeuvring unit 24 could as an alternative be provided with a maneuvering member i n the form of a joystick to be used for controlling the movement of the load suspension poi nt P i n the vertical and horizontal directions.

Each i ndividual directional-control-valve section 23 controls the magnitude and the direction of the flow of hydraulic fluid to a specific hydraulic cylinder 12 , 14 , 15 and thereby controls a specific crane function . For the sake of clarity, only the directional-control-valve section 23 for the lifting cylinder 12 is illustrated in Fig 6.

The directional-control-valve block 22 further comprises a shunt valve 26, which pumps excessive hydraulic fluid back to the reservoir 21 , and an electrically controlled dump valve 27, which can be made to return the entire hydraulic flow from the pump 20 directly back to the reservoir 21 .

In the illustrated example, the directional-control-valve block 22 is of load-sensing and pressure-compensating type, which implies that the magnitude of the hydraulic flow supplied to a hydraulic cylinder is always proportional to the position of the slide member in the corresponding directional-control-valve section 23. The directional-control-valve section 23 comprises a pressure limiter 28, a pressure compensator 29 and a directional-control-valve 30. Directional-control-valve blocks and directional-control-valve sections of this type are known and available on the market. Also other types of valve devices then the one here described may of course be used in a crane accordi ng to the present invention .

A load holding valve 31 is arranged between the respective hydraulic cylinder 1 2, 14, 15 and the associated directional- control-valve section 23, which load holding valve makes sure that the load will remain hangi ng when the hydraulic system runs out of pressure when the dump valve 27 is made to return the entire hydraulic flow from the pump 20 directly back to the reservoir 21 . Sensors 41 , 42 , 43, 44 (schematically illustrated i n Fig 6) are connected to the electronic control device 25 and configured to establish val ues of variables α, β , L, Θ (see Fig 4a) which are related to the prevailing position of the crane booms 1 1 , 13 of the crane boom system 10. In a crane 1 with the configuration illustrated in Figs 1 , 3-5 and 6, said variables comprise:

- a variable a representing the angle of inclination of the inner boom 1 1 ;

- a variable β representing the angle of inclination of the outer boom 1 3;

- a variable L representing the extension length of the outer boom 1 3; and

- a variable Θ representing the slewing angle of the column 7. The angles of inclination α, β , the extension length L and the slewing angle Θ together defi ne the position of the crane boom system 10 and the load suspension point P of the crane accordi ng to Figs 1 , 3-5 and 6, and these variables will consequently provide complete information about the prevailing position of the crane boom system 10 and the crane booms 1 1 , 13 incl uded therein .

In the example illustrated i n Fig 4a, the angle of i nclination a of the inner boom 1 1 is defi ned as the angle between the longitudinal axis of the inner boom 1 1 and the horizontal plane, whereas the angle of inclination β of the outer boom 13 is defined as the angle between the longitudinal axis of the outer boom 13 and the longitudinal axis of the inner boom 1 1 . The angle of inclination a of the inner boom 1 1 may for instance be established by means of a sensor 41 which continuously senses the position of the piston rod 12b in relation to the cylinder part 12a of the lifting cylinder 12, whereas the angle of inclination β of the outer boom 1 3 may be established by means of a sensor 42 which conti nuously senses the position of the piston rod 14b in relation to the cylinder part 14a of the outer boom cylinder 14. The angle of inclination a is a function of the extension position of the piston rod 1 2b of the lifting cylinder 12, and the angle of i nclination β is a function of the extension position of the piston rod 14b of the outer boom cylinder 14. Alternatively, these angles of inclination α, β could be established by means of suitable angle sensors, which directly sense the respective angle of inclination .

The extension length L of the outer boom 13 may for i nstance be established by means of a sensor 43 which continuously senses the position of the piston rod 15b in relation to the cylinder part 15a of the hydraulic cylinder 15. Alternatively, the extension length L could be established by means of a measuri ng device comprising an ultrasonic transmitter and an ultrasonic receiver of the type described in US 5 877 693 A or by means of any other suitable measuring device. The slewing angle Θ of the col umn 7 in relation to the crane base 6 is established by means of a sensor 44 which continuously senses the slewing position of the column .

The electronic control device 25 is connected to the above- mentioned sensors 41 , 42, 43, 44 in order to receive measuring signals from these sensors related to the angles of inclination a, β , the extension length L and the slewing angle Θ. Two different control modes, in the following denominated first and second control modes, are provided for the electronic control device 25. I n the first control mode the electronic control device 25 is configured to make the load suspension point P move along a trajectory defined by the above-mentioned control signals from the manoeuvring unit 24 while controlling the crane boom movements i n accordance with an ordi nary control strategy. The ordinary control strategy may be focused on the optimization of the lifting capacity of the crane 1 , in which case the electronic control device 25 is configured to make the crane booms 1 1 , 13 move into positions which will give as high lifting capacity as possi ble in each position assumed by the load suspension point P. As a further alternative, the ordinary control strategy may be focused on the minimization of the energy consumption of the crane 1 , in which case the electronic control device 25 is configured to effect crane boom movements which will give the lowest possible energy consumption . The ordinary control strategy may also be based on other criteria . The electronic control device 25 is configured to switch from the first control mode into the second control mode when it is established by the electronic control device 25 that the inner boom 1 1 is about to interfere with a predefined safety zone associated with a known obstacle 18 or about to i nterfere with an obstacle detected by means of one or more sensors 45 (schematically illustrated in Fig 6) connected to the electronic control device 25. The last-mentioned sensors 45 may for instance comprise one or more ultrasonic sensors mounted to the inner boom 1 1 and/or the outer boom 13. In the second control mode, the electronic control device 25 is configured to make the load suspension poi nt P move along the trajectory defined by the above-mentioned control signals from the manoeuvring unit 24 while controlling the crane boom movements i n accordance with an auxiliary control strategy i n which the first crane boom 1 1 is prevented from i nterfering with the safety zone or the detected obstacle. The auxiliary control strategy is mai nly focused on the positioning of the inner boom 1 1 in safe positions in relation to a known or detected obstacle within the working area of the crane 1 .

The electronic control device 25 may be configured to also take into account the position of the outer boom 13 i n relation to the safety zone or the detected obstacle in order to automatically prevent also the outer boom 13 from interfering with the safety zone or the detected obstacle.

The safety zone is preferably defined as a set of limit values Vaiimit for the angle of i nclination a of the inner boom 1 1 , wherei n each limit value Vanmit of the set of limit values is associated with a given slewing angle Θ of the col umn 7 and represents a limit for the allowed inclination of the inner boom 1 1 in a vertical plane downwards or upwards at the associated slewing angle Θ of the column 7.

The electronic control device 25 is configured to stop presently executed crane boom movements when it has been established by the electronic control device that the crane booms 1 1 , 1 3 of the crane boom system 1 0 cannot be positioned to move the load suspension point P along the trajectory defi ned by said control signals without the inner boom 1 1 interfering with the safety zone or the detected obstacle.

The electronic control device 25 is also, in a conventional manner, configured to prevent an execution of crane boom movements that would make the lifting moment of the crane 1 exceed a lifting moment maximum value M max representing a maximum allowed value for the lifting moment of the crane 1 . The electronic control device 25 is with advantage, in a conventional manner, adapted to convert the lifting moment maximum val ue M max into a corresponding value for the maximum allowed working pressure for the lifting cylinder 12. I n the embodiment illustrated in Fig 6, the crane 1 comprises a pressure sensor 32 which is arranged to measure the hydraulic pressure on the piston side of the lifting cylinder 12. The electronic control device 25 is connected to the pressure sensor 32 in order to receive measuring signals from this sensor related to said hydraulic pressure. The electronic control device 25 continuously reads the output signals from the pressure sensor 32 and compares the output signal from the pressure sensor with the established value of the maximum allowed working pressure for the lifting cylinder 1 2. If the pressure sensed by the pressure sensor 32 exceeds the established maximum allowed working pressure for the lifting cylinder 12, the electronic control device 25 delivers a signal to the dump valve 27, which dumps the hydraulic flow directly to the reservoir 21 , which results in that the hydraulic system runs out of pressure and that the presently executed crane boom movements are stopped . In this situation , the load 9 is held by means of the load holding valve 31 . In the embodiment illustrated in Figs 1 -5, the above-mentioned safety zone is associated with a known obstacle 18 in the form of the driver's cab of the lorry 4. As long as the col umn 7 is in such a rotational position in relation to the driver's cab 18 that the inner boom 1 1 may assume any angle of inclination a without i nterfering with the driver's cab, the electronic control device 25 is configured to apply the above-mentioned first control mode and control the crane boom movements i n accordance with the ordi nary control strategy. Figs 3a and 3b illustrates a situation i n which the inner boom 1 1 may assume any angle of inclination a without interfering with the driver's cab 18 but will collide with the driver's cab 18 if the crane boom system 10 is su bjected to a mere rotation towards the driver's cab by a rotation of the col umn 7. When the crane operator orders a movement of the load suspension poi nt P from the position illustrated in Figs 3a and 3b to the position illustrated in Figs 4a and 4b, i .e. a rotation of the crane boom system 1 0 towards the driver's cab 18 without any movement of the load suspension point P i n vertical direction , the electronic control device 25 will establish that the inner boom 1 1 is about to interfere with the safety zone associated with the driver's cab 18 and will consequently switch from the first control mode to the second control mode, whereupon the electronic control device 25 will control the crane boom movements in such a manner that the inner boom 1 1 is automatically raised and the angle of inclination β and the extension length L of the outer boom 1 3 are automatically modified so as to allow the inner boom 1 1 to run free of the driver's cab 18 and at the same time allow the load suspension poi nt P to follow the trajectory ordered by the crane operator. When the movement of the load suspension point P continues from the position illustrated in Figs 4a and 4b to the position illustrated in Figs 5a and 5b the electronic control device 25 will establish that the i nner boom 1 1 leaves the area above the safety zone associated with the driver's cab 18 and will then switch back to the first control mode and continue to control the crane boom movements in accordance with the ordinary control strategy, which implies that the angle of inclination a of the inner boom 1 1 and the angle of inclination β and the extension length L of the outer boom 13 are automatically modified .

The electronic control device 25 may be implemented by one single electronic control unit, as illustrated in Fig 6. However, the electronic control device 25 could as an alternative be implemented by two or more mutually co-operating electronic control units.

The invention is of course not in any way limited to the embodiments described above. On the contrary, several possibilities to modifications thereof should be apparent to a person skilled in the art without thereby deviating from the basic idea of the invention as defined in the appended claims. The control system of the crane may for instance have another design than the control system which is illustrated in Fig 6 and described above. Furthermore, the crane boom system of the crane could have another design than the crane boom system which is illustrated in drawings and described above.