EP3926105B1 - Agencement de pied stabilisateur et machine de travail mobile comportant un tel agencement de pied stabilisateur - Google Patents

Agencement de pied stabilisateur et machine de travail mobile comportant un tel agencement de pied stabilisateur Download PDF

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Publication number
EP3926105B1
EP3926105B1 EP20180757.5A EP20180757A EP3926105B1 EP 3926105 B1 EP3926105 B1 EP 3926105B1 EP 20180757 A EP20180757 A EP 20180757A EP 3926105 B1 EP3926105 B1 EP 3926105B1
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EP
European Patent Office
Prior art keywords
stabilizer leg
hydraulic
chamber
valve
piston
Prior art date
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EP20180757.5A
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German (de)
English (en)
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EP3926105A1 (fr
Inventor
Jan MIKAELSSON
Lars Rydahl
Mats LINDSTRÖM
Erik Nylander
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Hiab AB
Original Assignee
Hiab AB
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Priority to EP20180757.5A priority Critical patent/EP3926105B1/fr
Priority to DK20180757.5T priority patent/DK3926105T3/da
Publication of EP3926105A1 publication Critical patent/EP3926105A1/fr
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Publication of EP3926105B1 publication Critical patent/EP3926105B1/fr
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    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/08—Superstructures; Supports for superstructures
    • E02F9/085—Ground-engaging fitting for supporting the machines while working, e.g. outriggers, legs
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C23/00—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes
    • B66C23/62—Constructional features or details
    • B66C23/72—Counterweights or supports for balancing lifting couples
    • B66C23/78—Supports, e.g. outriggers, for mobile cranes
    • B66C23/80—Supports, e.g. outriggers, for mobile cranes hydraulically actuated

Definitions

  • the present invention relates to a stabilizer leg arrangement according to the preamble of claim 1 for supporting a mobile working machine against the ground.
  • the invention also relates to a mobile working machine comprising such a stabilizer leg arrangement.
  • a device according to the prior art is disclosed in WO 2013/120118 A1 .
  • a mobile working machine equipped with a load handling crane such as for instance a lorry having a hydraulic loader crane mounted on its chassis, is often provided with hydraulically actuated stabilizer legs for supporting the mobile working machine against the ground to thereby improve the stability of the mobile working machine against tipping.
  • a mobile working machine may be provided with means for detecting whether or not a stabilizer leg has reached an active supporting position in supporting contact with the ground.
  • the cylinder ratio C R is in its turn defined as the effective pressure area on the piston side of the hydraulic cylinder divided by the effective pressure area on the piston rod side of the hydraulic cylinder.
  • the differential pressure in the hydraulic cylinder of such a stabilizer leg may be determined by means of an electronic control device based on a first measuring value representing the hydraulic pressure on the piston side of the hydraulic cylinder and a second measuring value representing the hydraulic pressure on the piston rod side of the hydraulic cylinder.
  • the electronic control device may be configured to compare the established value of the differential pressure in the hydraulic cylinder with a given threshold value and establish that the stabilizer leg is in the active supporting position if the differential pressure is higher than the threshold value.
  • a high differential pressure resembling the differential pressure that is developed in the hydraulic cylinder when the stabilizer leg is pressed against the ground in the active supporting position may also be developed in the hydraulic cylinder in a situation when it has reached its advanced end position before the stabilizer leg has been pressed against the ground.
  • a system that is configured to use the value of the differential pressure in the hydraulic cylinder of the stabilizer leg in order to establish whether or not the stabilizer leg is in the active supporting position also has to include an additional sensor for detecting whether or not the hydraulic cylinder of the stabilizer leg is in its advanced end position.
  • the object of the present invention is to provide a new and favourable manner of detecting whether or not a stabilizer leg is in supporting contact with the ground.
  • the stabilizer leg arrangement comprises a support structure and a stabilizer leg carried by the support structure, the stabilizer leg being provided with a hydraulic cylinder, by means of which the stabilizer leg is moveable in relation to the support structure from a raised inactive position, in which the stabilizer leg is out of contact with the ground, to an active supporting position, in which the stabilizer leg is in supporting contact with the ground, wherein the hydraulic cylinder comprises:
  • the stabilizer leg arrangement further comprises a pressure sensor configured to generate a measuring value representing the hydraulic pressure in said first chamber, and an electronic control device connected to the pressure sensor, wherein the electronic control device is configured to establish information as to whether or not the stabilizer leg is in the active supporting position while taking into account said measuring value.
  • the stabilizer leg arrangement comprises a hydraulic system with:
  • the second chamber is configured to come into fluid communication with the first chamber through at least one flow channel of the hydraulic cylinder when the piston reaches the advanced end position or is on the verge of reaching this end position, wherein the piston is configured to keep the second chamber fluidly separated from the first chamber when the piston is in any other position in relation to the cylinder housing.
  • the load-holding valve has the form of a pilot-operated check valve and comprises a pilot line connected to the second hydraulic line, wherein the load-holding valve is configured to assume the open position when the hydraulic pressure in the second hydraulic line, and thereby in the pilot line, exceeds a predetermined level.
  • the load-holding valve is automatically controlled by the hydraulic pressure in the second hydraulic line, which corresponds to the hydraulic pressure in the second chamber of the hydraulic cylinder.
  • the hydraulic pressures in the first and second chambers of the hydraulic cylinder are equalized by the fluid communication through the above-mentioned flow channel of the hydraulic cylinder, which implies that the second chamber and the second hydraulic line will be subjected to the higher hydraulic pressure that has been generated in the first chamber.
  • the pilot-operated check valve will assume the open position under the effect of this higher hydraulic pressure and the first chamber is thereby connected to the reservoir via the directional control valve, which will result in a release of the hydraulic pressure in the first and second chambers and a return of the pilot-operated check valve to the closed position.
  • the hydraulic pressure in the first chamber will remain low and prevent an establishment that the stabilizer leg is in the active supporting position.
  • the stabilizer leg has already made contact with the ground at the moment when the piston reaches the advanced end position and the valve spool returns to the normal position. If the stabilizer leg is actually in contact with the ground when the pilot-operated check valve returns to the closed position, the load acting on the stabilizer leg via the support structure may cause the generation of an increased hydraulic pressure in the first chamber and make possible an establishment that the stabilizer leg is in the active supporting position.
  • the stabilizer leg arrangement When the load-holding valve has the form of a pilot-operated check valve with a pilot line connected to the second hydraulic line, there is no need for the stabilizer leg arrangement to include an additional pressure sensor for measuring the hydraulic pressure in the second chamber or in the second hydraulic line.
  • the electronic control device may be configured to establish that the stabilizer leg is in the active supporting position when the measuring value representing the hydraulic pressure in the first chamber is higher than a given threshold value.
  • the stabilizer leg arrangement may as an alternative be configured to establish that the stabilizer leg is in the active supporting position when the differential pressure in the hydraulic cylinder is higher than a given threshold value. In the latter case, the stabilizer leg arrangement has to be provided with an additional pressure sensor configured to generate a measuring value representing the hydraulic pressure in the second chamber of the hydraulic cylinder.
  • the load-holding valve is controlled by the electronic control device, wherein the electronic control device is configured to control the load-holding valve to assume the open position when a measuring value representing the hydraulic pressure in the second chamber is equal to the measuring value representing the hydraulic pressure in the first chamber in a situation when the valve spool of the directional control valve is in the normal position.
  • the stabilizer leg arrangement has to be provided with an additional pressure sensor configured to generate a measuring value representing the hydraulic pressure in the second chamber.
  • the electronic control device will make the load-holding valve assume the open position and the first chamber is thereby connected to the reservoir via the directional control valve, which will result in a release of the pressure in the first and second chambers.
  • the electronic control device may be configured to establish that the stabilizer leg is in the active supporting position when the measuring value representing the hydraulic pressure in the first chamber is higher than a given threshold value or, as an alternative, when the differential pressure in the hydraulic cylinder is higher than a given threshold value.
  • the electronic control device is configured, after said opening of the load-holding valve, to control the load-holding valve to return to the closed position when the load-holding valve has been open for a given period of time, preferably in the order of 1-3 seconds. If the stabilizer leg is not in supporting contact with the ground in this situation, the hydraulic pressure in the first chamber will remain low and prevent an establishment that the stabilizer leg is in the active supporting position. However, there is also a possibility that the stabilizer leg has already made contact with the ground at the moment when the piston reaches the advanced end position and the valve spool returns to the normal position.
  • the load acting on the stabilizer leg via the support structure may cause the generation of an increased hydraulic pressure in the first chamber and make possible an establishment that the stabilizer leg is in the active supporting position.
  • the invention also relates to a mobile working machine having the features defined in claim 14.
  • Fig 1 schematically illustrates a mobile working machine 1 provided with a stabilizer leg arrangement 2 according to an embodiment of the present invention for supporting the mobile working machine against the ground.
  • the mobile working machine 1 is a crane vehicle comprising a vehicle 3 and a hydraulic crane 4.
  • the crane 4 is mounted to a chassis 5 of the vehicle 3, either by being fixed directly to the chassis 5 or by being fixed to a subframe, which in its turn is fixed to the chassis 5.
  • the illustrated crane 4 comprises:
  • the above-mentioned second crane boom 10 is telescopically extensible by means of a hydraulic cylinder 12 in order to enable an adjustment of the extension length thereof.
  • the stabilizer leg arrangement 2 comprises a support structure 20.
  • the support structure 20 comprises a support beam 21 and two extension arms 22 mounted to the support beam 21 on opposite sides thereof.
  • the support beam 21 is fixedly connected to the chassis 5 of the vehicle 3.
  • the support beam 21 may be rigidly mounted to the crane base 6, wherein the support beam 21 is fixedly connected to the chassis 5 via the crane base 6.
  • the support beam 21 may as an alternative be mounted directly to the chassis 5, i.e. not directly connected to e.g. a crane.
  • Each extension arm 22 is telescopically extensible in order to allow an adjustment of the horizontal extension length thereof.
  • Each extension arm 22 is telescopically mounted to the support beam 21 so as to be axially slidable in relation to the support beam 21 in the longitudinal direction of the extension arm 22 in order to vary the horizontal extension length thereof.
  • Each extension arm 22 is horizontally moveable in relation to the support beam 21 by means of a hydraulic cylinder 23 or any other suitable type of linear actuator.
  • a stabilizer leg 25 is mounted to each extension arm 22 at an outer end thereof, wherein the stabilizer leg 25 is extensible in a vertical direction in relation to the extension arm 22.
  • Each stabilizer leg 25 comprises a foot plate 26, which is arranged at a lower end of the stabilizer leg.
  • each stabilizer leg 25 comprises a hydraulic cylinder 27, by means of which the stabilizer leg is manoeuvrable in relation to the extension arm 22 between a raised inactive position, in which the stabilizer leg is raised from the ground 13, and an active supporting position, in which the stabilizer leg is in supporting contact with the ground 13. In the active supporting position, the foot plate 26 of the stabilizer leg 25 is pressed against the ground 13.
  • each stabilizer leg 25 comprises a cylinder housing 30, which forms an upper part of the stabilizer leg, and a piston rod 31, which forms a lower part of the stabilizer leg.
  • the foot plate 26 is fixed to the lower end of the piston rod 31.
  • a hydraulic cylinder 27 suitable for use in a stabilizer leg 25 of a stabilizer leg arrangement according to the present invention are illustrated in Figs 2-15 .
  • the piston rod 31 of the hydraulic cylinder 27 is at its upper end fixed to a piston 32, which is movably received in an internal space 33 of the cylinder housing 30.
  • the piston 32 divides the internal space 33 of the cylinder housing into a first chamber 34 on a first side of the piston and a second chamber 35 on an opposite second side of the piston.
  • An annular sealing member 36 is arranged in an annular recess 37 in the envelop surface of the piston 32, wherein this sealing member 36 is in sliding and fluid-tight contact with a cylindrical inner wall 38 of the cylinder housing 30 in order to form a sealed interface between the piston 32 and the inner wall 38 of the cylinder housing.
  • the piston rod 31 extends through the second chamber 35, which implies that the above-mentioned second side of the piston 32 constitutes the piston rod side of the hydraulic cylinder 27 and that the above-mentioned first side of the piston 32 constitutes the piston side thereof.
  • the piston 32 is moveable in relation to the cylinder housing 30 to an advanced end position (see Figs 5, 6 , 8 and 12 ), in which the piston 32 abuts against a stop surface 40 at a lower end of the internal space 33 and in which the second chamber 35 has its minimum volume.
  • the second chamber 35 is configured to come into fluid communication with the first chamber 34 through at least one flow channel 41, 41', 41", 41′′′ in the hydraulic cylinder 27 when the piston 32 reaches the advanced end position or is on the verge of reaching this end position, wherein the piston 32 is configured to keep the second chamber 35 fluidly separated from the first chamber 34 when the piston 32 is in any other position in relation to the cylinder housing 30, i.e. when the piston 32 is not in or on the verge of reaching the advanced end position.
  • the above-mentioned flow channel 41 extends through the piston 32.
  • the piston 32 is provided with a valve member 42, which is moveable between a closed position (see Fig 4 , in which the valve member 42 obstructs fluid flow through the flow channel 41, and an open position (see Figs 5 and 6a ), in which the valve member 42 allows hydraulic fluid to flow through the flow channel 41 from the first chamber 34 to the second chamber 35.
  • a closed position see Fig 4
  • an open position see Figs 5 and 6a
  • the valve member 42 is configured to be automatically moved to the open position when the piston 32 reaches or is on the verge of reaching the advanced end position.
  • the valve member 42 is moveable from the closed position to the open position against the action of a spring member 43 and from the open position to the closed position by the action of the spring member 43.
  • the illustrated valve member 42 comprises:
  • the stop 47 is formed by an edge on the above-mentioned stop surface 40.
  • the stop 47 and the stop surface 40 may as an alternative be separated from each other.
  • the above-mentioned spring member 43 has the form of a helical compression spring, which at a first end abuts against a shoulder 48 on the head part 44 and at an opposite second end abuts against an end cap 49 that is fixed to a sleeve-shaped part 50 at an upper end of the flow channel 41. Hydraulic fluid is allowed to flow into the flow channel 41 through a passage 51 in the end cap 49.
  • valve member 42 may of course also have any other suitable design in addition to the design illustrated in Figs 4-6a .
  • the hydraulic cylinder is provided with a valve member 42' resembling the valve member illustrated in Fig 6a .
  • This valve member 42' is moveable to the open position in the same manner as the valve member 42 illustrated in Fig 6a .
  • this valve member 42' is not configured to co-operate with any spring member.
  • the valve member 42' illustrated in Fig 6b is provided with an axial channel 63, which is open at both ends and extends inside the valve member from the lower end of the valve member to the upper end thereof.
  • a piston 64 is provided at the upper end of the valve member 42', wherein this piston 64 is slidably received in an inner space of a valve housing 65 formed by a sleeve-shaped part 50 and an associated end cap 49.
  • the piston 64 divides this inner space into an upper chamber 66 and a lower chamber 67, wherein the upper chamber 66 is in fluid communication with the second chamber 35 through the channel 63 and the lower chamber 67 is in fluid communication with the first chamber 34 through a radially extending through hole 68 in the sleeve-shaped part 50 of the valve housing 65.
  • the above-mentioned flow channel 41' is formed as an axial groove in the cylindrical inner wall 38 of the cylinder housing 30.
  • This axial groove 41' has a larger extension in the axial direction of the cylinder housing 30 than the sealing member 36 to thereby allow the sealing member 36 to assume a position between the upper and lower ends of the groove 41' when the piston 32 is in the advanced end position, as illustrated in Fig 8 .
  • the upper end of the groove 41' is in fluid communication with the first chamber 34 and the lower end of the groove 41' in fluid communication with the second chamber 35.
  • hydraulic fluid is supplied to and discharged from the second chamber 35 through a feed and discharge channel 55 in an elongated and rigid pipe 56, which is fixed to the cylinder housing 30 at an upper end thereof and which extends axially through the first chamber 34.
  • an internal space 53 of the piston rod 31 is in fluid communication with the second chamber 35 through radially extending through holes 54 at the upper end of the piston rod.
  • the pipe 56 extends through an axial through hole 57 in the piston 32 and an inlet and outlet opening 58 is provided at the lower end of the pipe 56.
  • the pipe 56 has such a length that the inlet and outlet opening 58 is located in the internal space 53 of the piston rod 31 in all possible positions of the piston 32, i.e. also when the piston is in the advanced end position illustrated in Fig 12 .
  • the feed and discharge channel 55 is always in fluid communication with the second chamber 35 via the inlet and outlet opening 58 and the through holes 54 in order to allow hydraulic fluid to be fed into the second chamber 35 via the pipe 56 when the piston rod 31 and the foot plate 26 at the lower end of the piston rod are to be moved upwards in relation to the cylinder housing 30 and allow hydraulic fluid to be discharged from the second chamber 35 via the pipe 56 when the piston rod 31 and the foot plate 26 are to be moved upwards in relation to the cylinder housing.
  • the above-mentioned flow channel 41" is formed by a section 59 of the feed and discharge channel 55 at the lower end thereof and by at least one through hole 60 in the wall 61 of the pipe 56 at the upper end of this channel section 59.
  • the through hole 60 has such a position in the axial direction of the pipe 56 that it is received in the first chamber 34 when the piston 32 is in the advanced end position, as illustrated in Fig 12 .
  • the feed and discharge channel 55 is in fluid communication with the first chamber 34 via the through hole 60 in the pipe 56 and in fluid communication with the second chamber 35 via the inlet and outlet opening 58 in the pipe 56 and the through holes 54 in the piston rod 31, which implies that the first and second chambers 34, 35 are in fluid communication with each other via the above-mentioned section 59 of the feed and discharge channel 55.
  • the piston 32 is at a distance from the advanced end position and overlaps or is positioned above the through hole 60, there is no fluid communication between the first chamber 34 and the feed and discharge channel 55 and consequently no fluid communication between the first and second chambers 34, 35 via this channel.
  • the above-mentioned flow channel 41′′′ has the form of a hydraulic line arranged on the outside of the cylinder housing 30.
  • This hydraulic line 41′′′ is at a first end connected to the internal space 33 of the cylinder housing 30 via a first fluid port 69a in the cylindrical inner wall 38 of the cylinder housing and at a second end connected to the internal space 33 of the cylinder housing 30 via a second fluid port 69b in the cylinder housing 30.
  • the second fluid port 69b has such a position in the cylinder housing 30 that it is always in fluid communication with the second chamber 35 in all possible positions of the piston 32
  • the first fluid port 69a has such a position on the cylindrical inner wall 38 of the cylinder housing 30 that it is in fluid communication with the first chamber 34 when the piston 32 is in the advanced end position and disconnected from the first chamber 34 when the piston 32 is in any other position in relation to the cylinder housing 30.
  • the stabilizer leg arrangement 2 comprises a pressure sensor 70 (very schematically illustrated in Figs 13-15 ) configured to generate a measuring value V1 representing the hydraulic pressure in the first chamber 34 of the hydraulic cylinder 27.
  • this pressure sensor 70 is denominated first pressure sensor and the measuring value V1 is denominated first measuring value.
  • the stabilizer leg arrangement 2 also comprises an electronic control device 72.
  • the electronic control device 72 is connected to the first pressure sensor 70 in order to receive information about said first measuring value V1 from this sensor, wherein the electronic control device 72 is configured to establish information as to whether or not the stabilizer leg 25 is in the active supporting position while taking into account this measuring value V1.
  • the possibility for the electronic control device 72 to establish this information based on the first measuring value V1 from the first pressure sensor 70, without any additional measuring value from e.g. a length sensor, is due to the fact that the hydraulic pressures in the first and second chambers 34, 35 of the hydraulic cylinder 27 are equalized by the fluid communication through the above-mentioned flow channel 41, 41', 41", 41′′′ when the piston 32 reaches the advanced end position or is on the verge of reaching this end position.
  • the electronic control device 72 may be implemented by one single electronic control unit or by two or more mutually cooperating electronic control units.
  • the hydraulic system 80 comprises a hydraulic fluid reservoir 81, a pump 82 and a directional control valve 83, wherein the directional control valve is provided with a pressure port P and a return port R.
  • the pump 82 is configured to pump hydraulic fluid from the reservoir 81 to the pressure port P.
  • the return port R is connected to the reservoir 81 in order to allow hydraulic fluid to be returned from the directional control valve 83 to the reservoir via the return port.
  • the first chamber 34 of the hydraulic cylinder 27 is connected to the directional control valve 83 through a first hydraulic line 84 and the second chamber 35 is connected to the directional control valve 83 through a second hydraulic line 85.
  • the directional control valve 83 is provided with a valve spool 88, which is moveable between:
  • valve spool 88 is shown in the normal position. In the examples illustrated in Figs 13-15 , the valve spool 88 will be moved from the normal position to the first working position by being moved to the left under the effect of an actuating force acting on the valve spool 88 in a first direction, and from the normal position to the second working position by being moved to the right under the effect of an actuating force acting on the valve spool 88 in an opposite second direction.
  • the valve spool 88 is configured to automatically return to the normal position on removal of the actuating force.
  • An operator may control the directional control valve 83 and thereby the movement of the stabilizer leg 25 in a conventional manner by actuating a manoeuvring member of a manoeuvring unit.
  • a load-holding valve 86, 86' is arranged in the first hydraulic line 84 and shiftable between a closed position, in which the load-holding valve 86, 86' prevents fluid flow from the first chamber 34 to the directional control valve 83 through the first hydraulic line 84, and an open position, in which the load-holding valve 86, 86' allows fluid flow from the first chamber 34 to the directional control valve 83 through the first hydraulic line 84.
  • the load-holding valve 86 has the form of a pilot-operated check valve and comprises a pilot line 87 connected to the second hydraulic line 85.
  • the load-holding valve 86 is configured to assume the open position and allow discharge of hydraulic fluid from the first chamber 34 when the hydraulic pressure in the second hydraulic line 85, and thereby in the pilot line 87, exceeds a predetermined level.
  • the electronic control device 72 is configured to compare the above-mentioned first measuring value V1 with a given threshold value, wherein a measuring value V1 lower than the threshold value implies that the stabilizer leg 25 is not in the active supporting position.
  • the electronic control device 72 is in this case configured to establish that the stabilizer leg 25 is in the active supporting position if it is established by the electronic control device that the first measuring value V1 is higher than the threshold value.
  • a second pressure sensor 71 is configured to generate a second measuring value V2 representing the hydraulic pressure in the second chamber 35 of the hydraulic cylinder 27, wherein the electronic control device 72 is connected to the second pressure sensor 71 in order to receive information about said second measuring value V2 from this sensor.
  • the electronic control device 72 is configured to establish the magnitude of the differential pressure P diff in the hydraulic cylinder 27 based on the first and second measuring values V1, V2 from the first and second pressure sensors 70, 71 and compare the established value of the differential pressure P diff in the hydraulic cylinder 27 with a given threshold value, wherein a differential pressure P diff lower than the threshold value implies that the stabilizer leg 25 is not in the active supporting position.
  • the electronic control device 72 is in this case configured to establish that the stabilizer leg 25 is in the active supporting position if it is established by the electronic control device that the differential pressure P diff is higher than the threshold value.
  • the load-holding valve 86' has the form of an electrically controlled valve that is controlled by the electronic control device 72.
  • a second pressure sensor 71 is configured to generate a second measuring value V2 representing the hydraulic pressure in the second chamber 35 of the hydraulic cylinder 27, wherein the electronic control device 72 is connected to the second pressure sensor 71 in order to receive information about said second measuring value V2 from this sensor.
  • the electronic control device 72 is configured to compare the first and second measuring values V1, V2 and control the load-holding valve 86' to assume the open position if it is established by the electronic control device 72 that the second measuring value V2 is equal to the first measuring value V1 in a situation when the valve spool 88 of the directional control valve 83 is in the normal position.
  • the electronic control device 72 is preferably configured, after said opening of the load-holding valve 86', to control the load-holding valve 86' to return to the closed position when the load-holding valve 86' has been open for a given period of time, for instance in the order of 1-3 seconds.
  • the electronic control device 72 may be configured to compare the first measuring value V1 with a given threshold value, wherein a measuring value V1 lower than the threshold value implies that the stabilizer leg 25 is not in the active supporting position.
  • the electronic control device 72 is in this case configured to establish that the stabilizer leg 25 is in the active supporting position if it is established by the electronic control device that the first measuring value V1 is higher than the threshold value.
  • the electronic control device 72 may, as an alternative, be configured to establish the magnitude of the differential pressure P diff in the hydraulic cylinder 27 based on the first and second measuring values V1, V2 and compare the established value of the differential pressure P diff with a given threshold value, wherein a differential pressure P diff lower than the threshold value implies that the stabilizer leg 25 is not in the active supporting position.
  • the electronic control device 72 is in the latter case configured to establish that the stabilizer leg 25 is in the active supporting position if it is established by the electronic control device that the differential pressure P diff is higher than the threshold value.
  • the stabilizer leg arrangement 2 is provided with a stabilizer leg 25 of telescopic type where the hydraulic cylinder 27 is configured to move the stabilizer leg between the raised inactive position and the active supporting position by extending and retracting the stabilizer leg vertically in the axial direction of the stabilizer leg.
  • the stabilizer leg included in the stabilizer leg arrangement of the present invention may as an alternative be a so-called flap-down stabilizer leg, for instance of the type disclosed in GB 2 388 582 A or GB 1 099 147 A , where the hydraulic cylinder of the stabilizer leg is configured to move the stabilizer leg from the raised inactive position to the active supporting position by deploying the stabilizer leg downwards and from the active supporting position to the raised inactive position to by folding the stabilizer leg upwards.

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  • Engineering & Computer Science (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • General Engineering & Computer Science (AREA)
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  • Mechanical Engineering (AREA)
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Claims (15)

  1. Agencement de pied stabilisateur comprenant :
    - une structure de support (20) ;
    - un pied stabilisateur (25) porté par la structure de support (20), le pied stabilisateur (25) étant doté d'un vérin hydraulique (27), au moyen duquel le pied stabilisateur (25) est mobile par rapport à la structure de support (20) à partir d'une position inactive levée, dans laquelle le pied stabilisateur (25) n'est pas en contact avec le sol, vers une position de support active, dans laquelle le pied stabilisateur (25) est en contact de support avec le sol, dans lequel le vérin hydraulique (27) comprend :
    • un corps de vérin (30) présentant un espace interne (33),
    • un piston (32) reçu mobile dans ledit espace interne (33) et configuré pour diviser cet espace (33) en une première chambre (34) sur un premier côté du piston (32) et une deuxième chambre (35) sur un deuxième côté opposé du piston (32), et
    • une tige de piston (31) fixée au piston (32) et s'étendant à travers la deuxième chambre (35), le piston (32) étant mobile par rapport au corps de vérin (30) vers une position d'extrémité avancée, dans laquelle le piston (32) est en butée contre une surface d'arrêt (40) dans l'espace interne (33) et dans laquelle la deuxième chambre (35) présente son volume minimum ;
    - un capteur de pression (70) configuré pour générer une valeur de mesure (V1) représentant la pression hydraulique dans la première chambre (34) ;
    - un dispositif de commande électronique (72) connecté au capteur de pression (70), dans lequel le dispositif de commande électronique (72) est configuré pour établir des informations quant au fait de savoir si le pied stabilisateur (25) est ou non dans la position de support active tout en prenant en compte ladite valeur de mesure (V1) ;
    - un système hydraulique (80) comprenant un distributeur (83) auquel les première et deuxième chambres (34, 35) sont reliées, un réservoir (81) de fluide hydraulique, une pompe (82) pour pomper le fluide hydraulique à partir du réservoir (81) vers un orifice de pression (P) du distributeur (83), une première conduite hydraulique (84) par l'intermédiaire de laquelle la première chambre (34) est reliée au distributeur (83) et une deuxième conduite hydraulique (85) par l'intermédiaire de laquelle la deuxième chambre (35) est reliée au distributeur (83), dans lequel le distributeur (83) présente un orifice de retour (R) relié au réservoir (81) et est doté d'un distributeur à tiroir (88), qui est mobile entre :
    • une première position de travail, dans laquelle l'orifice de pression (P) est relié à la première conduite hydraulique (84) et l'orifice de retour (R) est relié à la deuxième conduite hydraulique (85),
    • une deuxième position de travail, dans laquelle l'orifice de pression (P) est relié à la deuxième conduite hydraulique (85) et l'orifice de retour (R) est relié à la première conduite hydraulique (84), et
    • une position normale, dans laquelle l'orifice de pression (P) est détaché des première et deuxième conduites hydrauliques (84, 85) ; et
    - une soupape de maintien de charge (86 ; 86') agencée dans la première conduite hydraulique (84) et déplaçable entre une position fermée, dans laquelle la soupape de maintien de charge (86 ; 86') est configurée pour empêcher un écoulement de fluide à partir de la première chambre (34) vers le distributeur (83) par l'intermédiaire de la première conduite hydraulique (84), et une position ouverte, dans laquelle la soupape de maintien de charge (86 ; 86') est configurée pour permettre un écoulement de fluide à partir de la première chambre (34) vers le distributeur (83) par l'intermédiaire de la première conduite hydraulique (84),
    caractérisé en ce :
    - que l'orifice de retour (R) du distributeur (83) est relié à la première conduite hydraulique (84) dans la position normale du distributeur à tiroir (88) ; et
    - que le vérin hydraulique (27) est doté d'au moins un canal d'écoulement (41 ; 41' ; 41" ; 41‴) par l'intermédiaire duquel la deuxième chambre (35) est configurée pour venir en communication fluidique avec la première chambre (34) lorsque le piston (32) atteint la position d'extrémité avancée ou est sur le point d'atteindre cette position d'extrémité, dans lequel le piston (32) est configuré pour maintenir la deuxième chambre (35) fluidiquement séparée de la première chambre (34) lorsque le piston (32) est dans n'importe quelle autre position par rapport au corps de vérin (30) .
  2. Agencement de pied stabilisateur selon la revendication 1, caractérisé en ce que la soupape de maintien de charge (86) a la forme d'un clapet antiretour à commande pilote et comprend une conduite pilote (87) reliée à la deuxième conduite hydraulique (85), dans lequel la soupape de maintien de charge (86) est configurée pour occuper la position ouverte lorsque la pression hydraulique dans la deuxième conduite hydraulique (85), et ainsi dans la conduite pilote (87), dépasse un niveau prédéterminé.
  3. Agencement de pied stabilisateur selon la revendication 1 ou 2, caractérisé en ce que le dispositif de commande électronique (72) est configuré pour établir que le pied stabilisateur (25) est dans la position de support active s'il est établi par le dispositif de commande électronique que la valeur de mesure (V1) représentant la pression hydraulique dans la première chambre (34) est plus élevée qu'une valeur de seuil donnée.
  4. Agencement de pied stabilisateur selon la revendication 1 ou 2, caractérisé en ce que l'agencement de pied stabilisateur (2) comprend un autre capteur de pression (71) configuré pour générer une valeur de mesure (V2) représentant la pression hydraulique dans la deuxième chambre (35), dans lequel le dispositif de commande électronique (72) est relié à ce capteur de pression (71) et configuré pour établir que le pied stabilisateur (25) est dans la position de support active s'il est établi par le dispositif de commande électronique que la pression différentielle (Pdiff) dans le vérin hydraulique (27) est plus élevée qu'une valeur de seuil donnée.
  5. Agencement de pied stabilisateur selon la revendication 1, caractérisé en ce :
    - que l'agencement de pied stabilisateur (2) comprend un autre capteur de pression (71) configuré pour générer une valeur de mesure (V2) représentant la pression hydraulique dans la deuxième chambre (35), dans lequel le dispositif de commande électronique (72) est relié à ce capteur de pression (71) ; et
    - que la soupape de maintien de charge (86') est commandée par le dispositif de commande électronique (72), dans lequel le dispositif de commande électronique (72) est configuré pour commander la soupape de maintien de charge (86') pour occuper la position ouverte s'il est établi par le dispositif de commande électronique (72) que la valeur de mesure (V2) représentant la pression hydraulique dans la deuxième chambre (35) est égale à la valeur de mesure (V1) représentant la pression hydraulique dans la première chambre (34) dans une situation dans laquelle le distributeur à tiroir (88) du distributeur (83) est dans la position normale.
  6. Agencement de pied stabilisateur selon la revendication 5, caractérisé en ce que le dispositif de commande électronique (72) est configuré, après ladite ouverture de la soupape de maintien de charge (86'), pour commander la soupape de maintien de charge (86') pour qu'elle revienne vers la position fermée lorsque la soupape de maintien de charge (86') a été ouverte pendant une période de temps donnée, de préférence de l'ordre de 1-3 secondes.
  7. Agencement de pied stabilisateur selon la revendication 5 ou 6, caractérisé en ce que le dispositif de commande électronique (72) est configuré pour établir que le pied stabilisateur (25) est dans la position de support active s'il est établi par le dispositif de commande électronique que la valeur de mesure (V1) représentant la pression hydraulique dans la première chambre (34) est plus élevée qu'une valeur de seuil donnée.
  8. Agencement de pied stabilisateur selon la revendication 5 ou 6, caractérisé en ce que le dispositif de commande électronique (72) est configuré pour établir que le pied stabilisateur (25) est dans la position de support active s'il est établi par le dispositif de commande électronique que la pression différentielle (Pdiff) dans le vérin hydraulique (27) est plus élevée qu'une valeur de seuil donnée.
  9. Agencement de pied stabilisateur selon l'une quelconque des revendications 1-8, caractérisé en ce que ledit canal d'écoulement (41) s'étend à travers le piston (32), et que le piston (32) est doté d'un élément de soupape (42), qui est mobile entre une position fermée, dans laquelle l'élément de soupape (42) est configuré pour empêcher un écoulement de fluide à travers le canal d'écoulement (41), et une position ouverte, dans laquelle l'élément de soupape (42) est configuré pour permettre un écoulement de fluide à travers le canal d'écoulement (41), dans lequel l'élément de soupape (42) est configuré pour être déplacé automatiquement vers la position ouverte lorsque le piston (32) atteint ou est sur le point d'atteindre la position d'extrémité avancée.
  10. Agencement de pied stabilisateur selon la revendication 9, caractérisé en ce que l'élément de soupape (42) est mobile à partir de la position fermée vers la position ouverte à l'encontre de l'action d'un élément de ressort (43) et à partir de la position ouverte vers la position fermée par l'action de l'élément de ressort (43).
  11. Agencement de pied stabilisateur selon la revendication 9 ou 10, caractérisé en ce que l'élément de soupape (42) comprend :
    - une partie tête (44), qui est configurée pour être en contact étanche avec un siège de soupape (45) lorsque l'élément de soupape (42) est dans la position fermée et empêcher ainsi un écoulement de fluide à travers le canal d'écoulement (41) ; et
    - une partie tige (46) allongée, qui est fixée à la partie tête (44) et s'étend à travers ledit canal d'écoulement (41), dans lequel la partie tige (46) est configurée pour venir en contact avec une butée (47) dans l'espace interne (33) lorsque le piston (32) est sur le point d'atteindre la position d'extrémité avancée pour pousser ainsi la partie tête (44) à distance du siège de soupape (45).
  12. Agencement de pied stabilisateur selon l'une quelconque des revendications 1-8, caractérisé en ce que
    ledit canal d'écoulement (41') est formé comme une rainure axiale dans une paroi intérieure (38) du corps de vérin (30).
  13. Agencement de pied stabilisateur selon l'une quelconque des revendications 1-8, caractérisé en ce que
    ledit canal d'écoulement (41''') a la forme d'une conduite hydraulique agencée sur l'extérieur du corps de vérin (30).
  14. Machine de travail mobile avec un châssis (5), caractérisée en ce que la machine de travail mobile (1) comprend un agencement de pied stabilisateur (2) selon l'une quelconque des revendications 1-13, dans laquelle la structure de support (20) de l'agencement de pied stabilisateur (2) est reliée au châssis (5).
  15. Machine de travail mobile selon la revendication 14, caractérisée en ce que la machine de travail mobile (1) comprend une grue hydraulique (4) montée sur le châssis (5).
EP20180757.5A 2020-06-18 2020-06-18 Agencement de pied stabilisateur et machine de travail mobile comportant un tel agencement de pied stabilisateur Active EP3926105B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP20180757.5A EP3926105B1 (fr) 2020-06-18 2020-06-18 Agencement de pied stabilisateur et machine de travail mobile comportant un tel agencement de pied stabilisateur
DK20180757.5T DK3926105T3 (da) 2020-06-18 2020-06-18 Stabilisatorbenarrangement og mobil arbejdsmaskine omfattende et sådant stabilisatorbenarrangement

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP20180757.5A EP3926105B1 (fr) 2020-06-18 2020-06-18 Agencement de pied stabilisateur et machine de travail mobile comportant un tel agencement de pied stabilisateur

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EP3926105A1 EP3926105A1 (fr) 2021-12-22
EP3926105B1 true EP3926105B1 (fr) 2022-11-16

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DK (1) DK3926105T3 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN116692667B (zh) * 2023-07-26 2024-03-22 青岛新世纪预制构件有限公司 一种装配式建筑预制构件的吊装装置

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1419609A (fr) 1964-04-25 1965-12-03 Yumbo Dispositif stabilisateur à béquilles ou analogues, formant support d'appui auxiliaire au sol pour véhicule roulant à l'arrêt et ses diverses applications
DE3271763D1 (en) * 1982-06-30 1986-07-24 Hydro Geraetebau Gmbh & Co Kg Hydraulic support arrangements
GB2388582B (en) 2002-05-13 2005-08-10 Niftylift Ltd Stabiliser leg
EP1518768A1 (fr) * 2003-09-24 2005-03-30 Sörensen Hydraulik Zweigniederlassung, Ulfborg, Filial af Sörensen Hydraulik GmbH, Tyskland Dispositif de soutien pour plateformes
AU2013220952B2 (en) * 2012-02-13 2016-05-19 Palfinger Ag Support device for a vehicle

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DK3926105T3 (da) 2023-02-13
EP3926105A1 (fr) 2021-12-22

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