EP0388641B1 - Hydraulikanlage für Baumaschinen, insbesondere für Radlader, Schlepper u. dgl. - Google Patents

Hydraulikanlage für Baumaschinen, insbesondere für Radlader, Schlepper u. dgl. Download PDF

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Publication number
EP0388641B1
EP0388641B1 EP90103203A EP90103203A EP0388641B1 EP 0388641 B1 EP0388641 B1 EP 0388641B1 EP 90103203 A EP90103203 A EP 90103203A EP 90103203 A EP90103203 A EP 90103203A EP 0388641 B1 EP0388641 B1 EP 0388641B1
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EP
European Patent Office
Prior art keywords
pressure
valve
hydraulic
line
hydraulic system
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP90103203A
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German (de)
English (en)
French (fr)
Other versions
EP0388641A2 (de
EP0388641A3 (de
Inventor
Wolfgang Dipl.-Ing. Reich
Franz-Werner Dr.-Ing. Adrian
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hanomag AG
Original Assignee
Hanomag AG
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Filing date
Publication date
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Publication of EP0388641A2 publication Critical patent/EP0388641A2/de
Publication of EP0388641A3 publication Critical patent/EP0388641A3/de
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Publication of EP0388641B1 publication Critical patent/EP0388641B1/de
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Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2217—Hydraulic or pneumatic drives with energy recovery arrangements, e.g. using accumulators, flywheels
    • 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
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2203—Arrangements for controlling the attitude of actuators, e.g. speed, floating function
    • E02F9/2207—Arrangements for controlling the attitude of actuators, e.g. speed, floating function for reducing or compensating oscillations
    • 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
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/226—Safety arrangements, e.g. hydraulic driven fans, preventing cavitation, leakage, overheating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/021—Installations or systems with accumulators used for damping

Definitions

  • the invention relates to a hydraulic system for construction machinery, in particular wheel loaders, tractors and. The like.
  • a work tool in particular a loading shovel
  • a main line leading from a pressure source via a control valve to the hydraulic cylinders being provided for actuating the hydraulic cylinders, from which a connecting line leading to at least one hydraulic accumulator branches off into the one downstream of the control valve switchable shut-off valve is arranged.
  • the work tool that is to say in particular the loading shovel, is raised, lowered, tilted, etc., via the manually actuated control valve, goods being able to be picked up and tipped over again at another point using the loading shovel.
  • a return line for the hydraulic medium is of course also provided, but is arranged and used in a known manner.
  • a hydraulic system of the type described above is known from DE-PS 28 56 583.
  • hydraulic cylinders for lifting and lowering the loading shovel hydraulic cylinders for tilting the loading shovel can of course also be provided in a further partial circle. Additional tools can also be switched via the control valve.
  • This hydraulic system is equipped with a damping system, which has the task of damping the pitching vibrations of a wheel loader with a loaded shovel at higher driving speeds.
  • a connecting line branches off from the main line between the control valve and the hydraulic cylinder, which leads to one or more hydraulic accumulators, which are provided by an air or gas cushion are biased to a gas side pressure of about 15 to 20 bar.
  • a switchable shut-off valve is provided in this connecting line, which can be switched by hand.
  • a throttle can also be provided in the connecting line to the hydraulic accumulator.
  • the manual actuation of the switchable shut-off valve allows the damping circuit formed by the hydraulic accumulator to be consciously switched on or off in order to consciously change the damping properties as required. If the construction machine is working in a stationary state and, for example, fills the loading shovel, it makes sense to design the system of wheel loader and loading shovel as rigidly as possible. B. the loading shovel can be kept precisely plan when entering the goods to be picked up and does not sink down into the goods.
  • the hydraulic accumulators are shut off from the main line because the switchable shut-off valve is in its closed position. As a result, the hydraulic accumulators cannot be acted upon by the high tear-off pressure and therefore cannot be overloaded.
  • the hydraulic cylinders are against incorrect operation of the Manually switchable shut-off valve, however, is not protected. When properly operated, however, the shut-off valve is closed.
  • the loading shovel is tilted and lifted, the lifting movement being ended by corresponding actuation of the control valve.
  • the carrying pressure in the hydraulic cylinders is then established, which is determined by the weight of the loading shovel and the weight of the material picked up in the loading shovel. This wearing pressure can be up to 100 or 120 bar.
  • the switchable shut-off valve is switched over manually or automatically at a time which can be selected by the driver in order to establish a connection between the two parts of the connecting line, so that the hydraulic cylinders with the carrying pressure of about 100 bar with the hydraulic accumulator or hydraulic accumulators, in which only the gas-side preload pressure of the order of 15 to 20 bar prevails, but in extreme cases the liquid-side pressure can also be 0 bar.
  • hydraulic fluid flows out of the hydraulic cylinders in the direction of the hydraulic accumulator (s) until the corresponding pressure equalization has taken place.
  • the damping system is activated. If you do not switch this damping system on and off manually, but instead controls the switchable shut-off valve depending on the driving speed, there is a risk that the driver will be surprised by the falling of the loading shovel when a certain driving speed is exceeded. This lowering of the loading shovel is uncomfortable and has the disadvantages already described.
  • the invention has for its object to improve a hydraulic system of the type described in such a way that despite the switching on and off of a damping system, which has hydraulic accumulator, to the hydraulic cylinders of the working tool there is no significant drop in the working tool when the damping system is switched on.
  • a filling line bridging the shut-off valve which connects the main line to the hydraulic accumulator, and in that a pressure reducing valve is arranged in the filling line.
  • the invention is based on the idea of charging the hydraulic accumulator (s), which are normally only charged with their preload pressure, to a higher pressure in the course of a filling process of the working tool or the loading shovel, which corresponds at least approximately to the expected carrying pressure connecting the hydraulic cylinder and the hydraulic accumulator via the shut-off valve, there is no significant quantity compensation of hydraulic fluid between the hydraulic cylinder and the hydraulic accumulator, and thus the carrying pressure in the hydraulic cylinders when the damping system is switched on changed as little as possible.
  • the carrying pressure will depend on the degree of filling of the working tool, on the specific weight of the load and on the weight of the loading shovel, so that this carrying pressure can fluctuate within certain limits for a certain construction machine over several working cycles. However, these fluctuations are not too great. If the pressure reducing valve is set to a relatively high pressure and the loading shovel is only partially filled during a certain filling process, it can even happen that the boost pressure in the hydraulic cylinders is greater than the carrying pressure in the hydraulic cylinders. When connecting the hydraulic cylinders to the hydraulic accumulators, however, this is not disadvantageous because the loading shovel can then only be raised slightly at most, and in any case falling down is avoided.
  • the filling line and the pressure reducing valve must provide such cross-sections so that the hydraulic accumulators can be charged at the beginning of a filling process, in particular during the tearing-off phase and perhaps also during the subsequent tilting and lifting process.
  • These functions are performed by the pressure reducing valve, which can be implemented in various ways. It is important that the pressure reducing valve limits the pressure in the filling line to the hydraulic accumulators and, on the other hand, ensures that the boost pressure remains in the hydraulic accumulators so that as little pressure compensation as possible occurs in the subsequent connection between hydraulic cylinders and hydraulic accumulators.
  • a check valve can also be provided in this part of the filling line between the pressure reducing valve and the hydraulic accumulators.
  • the filling line must bridge the shut-off valve in any case, ie it can either be before or after Control valve connected to the main line.
  • the various connection options depend on the main purpose of the construction machinery concerned and the desired result.
  • the deliberate pressure charging of the hydraulic accumulator to a boost pressure which corresponds approximately to the expected carrying pressure of the working tool makes it advantageously possible that the manually switchable shut-off valve can also be controlled depending on the driving speed or depending on the tilting angle of the working tool.
  • the driver is no longer unpleasantly surprised. Rather, he only notes that, on the one hand, for example, leveling work can be carried out with a fixed loading shovel and, on the other hand, the pitching vibrations are very well damped at higher driving speeds.
  • the pressure reducing valve can be set to the carrying pressure of the hydraulic cylinders.
  • the setting is expediently carried out to an average expected wearing pressure or to the maximum possible wearing pressure of the hydraulic cylinders.
  • This boost pressure is of the order of 100 to 120 bar, that is to say in a pressure range for which the hydraulic accumulators are designed without overloading or overstressing taking place.
  • the pressure reducing valve can be designed as a pressure limiting valve or as a pressure cutter.
  • a pressure relief valve is understood to mean such a valve which only allows a limited pressure in the filling line in the direction of the hydraulic accumulator and when this adjustable pressure is exceeded, hydraulic medium is discharged into an oil reservoir via a return line. This return of the hydraulic fluid can make itself felt in a noteworthy flow, but on the other hand can only absorb a leak oil rate.
  • the pressure reducing valve is also possible to design the pressure reducing valve as a pressure cutter.
  • Such a pressure cutter is understood to mean a valve which closes when the set pressure is reached, that is to say separates the parts of the filling line connected on both sides from one another and closes off on both sides.
  • Such a pressure cutter can also be understood as a shut-off valve or two-way valve, a passage being provided in one position, while a closing function is achieved in the other position.
  • the pressure reducing valve can either control itself or can be controlled via a control element, which can in particular be pressure-dependent.
  • the filling line also bridges the control valve and is connected to the main line upstream of the control valve, the particular advantage is achieved that the highest pressures occurring in the main line are always used to charge the hydraulic accumulators. Such pressures occur, for example, during the tearing-off phase of the filling process when the loading shovel is still tilted at the same time.
  • the utilization of the highest pressures in the main line for charging the hydraulic accumulator ensures that the charging process takes place in a comparatively very short time, so that the cross sections in the filling line and in the pressure reducing valve can be chosen accordingly smaller and in any case it is ensured that even one exceptionally short detachment process, the intended boost pressure in the hydraulic accumulator is safely achieved.
  • the pressure reducing valve can be connected to an oil reservoir via a return line, so that Hydraulic medium, in particular as leak oil, is returned to the tank or oil reservoir.
  • the pressure reducing valve is designed to be flow-through as a function of time or is provided with a throttle which is particularly adjustable. This time dependency makes sense, so that in this way, depending on the length of the tear-off phase, differently high charging pressures can be stored in the hydraulic accumulators.
  • a short breakaway phase indicates that the loading shovel is only partially filled, so that the carrying pressure is lower in this case and a lower charging pressure in the hydraulic cylinders corresponds most closely to this lower carrying pressure.
  • a longer breakaway phase indicates more difficult working conditions, whereby a higher level of bucket filling is also to be expected, a higher loading weight occurs, and thus a correspondingly higher carrying pressure is best maintained by a higher loading pressure.
  • the pressure reducing valve can be designed as a solenoid valve and can be controlled via a pressure switch in the part of the filling line leading to the hydraulic accumulator.
  • the pressure reducing valve is normally open, ie when the pressure in the filling line rises. If the intended boost pressure is reached in the branch of the filling line leading to the hydraulic accumulators, then the pressure switch switches over the solenoid valve or pressure reducing valve so that the part of the filling line leading to the hydraulic accumulator is shut off. The required boost pressure is then available in the hydraulic accumulators.
  • the pressure reducing valve can also be controlled, for example, as a function of time, if it is to be expected or ensured that the intended boost pressure is approximately constant over a certain period of time.
  • the switchable shut-off valve which connects the hydraulic cylinders to the hydraulic accumulators, to be designed as a solenoid valve controlled as a function of travel speed or as a function of the tilt angle of the working tool.
  • the shift point can be set so that it can only be exceeded in second gear. This ensures, on the one hand, that moving a wheel loader into an item to be picked up, which experience has shown to take place in first gear, cannot result in the damping system being switched on. As a result, the loading shovel remains relatively stiff during the retraction and the tearing process, as u. a. is also desirable for leveling purposes. Even spinning the drive wheels during the tearing phase in first gear cannot lead to the hydraulic accumulators being connected to the hydraulic cylinders. This means that even spinning the wheels in first gear cannot lead to a connection between the hydraulic cylinder and hydraulic accumulator. Rather, this connection is only made possible in second gear, in which a spinning of the wheels is no longer possible due to a correspondingly smaller torque.
  • the pressure reducing valve which is designed as a pressure cutter, can also be designed to be pulse-width-modulated, ie the boost pressure in the hydraulic accumulators can be set or reached via a time dependency and the width of a control pulse.
  • the hydraulic system shown in FIG. 1 has a pressure source (not shown), in particular a continuously driven pump, from which a main line 1 leads to hydraulic cylinders 3 via a manually operated control valve 2 of a conventional type.
  • the hydraulic cylinders 3 can be acted upon on both sides.
  • the main line 1 leads to the side of the pistons of the hydraulic cylinders 3, which are acted upon during the lifting process of the loading shovel, which is confirmed via the hydraulic cylinders 3 and is not shown.
  • the control valve 2 has a valve unit 4 for raising and lowering the loading shovel, the four positions shown being possible for the lines concerned.
  • a valve unit 5 in the control valve 2 serves to carry out tilting movements on the loading shovel via the lines 6 and 7.
  • a valve unit 8 allows the actuation of additional devices, for example a tree clip via the control valve 2.
  • a line 9 leads from the control valve 2 to the other side the piston of the hydraulic cylinder 3, a lowering process being initiated via this line 9.
  • a return line 10 leads in a known manner from the control valve 2 to an oil reservoir 11, which is usually also referred to as a tank.
  • One or more hydraulic accumulators 12 are provided, which are preloaded to a preload pressure of the order of 15 to 20 bar via an air or gas cushion, not shown.
  • a connecting line 13 leads from the main line 1 between the control valve 2 and the hydraulic cylinders 3 via a switchable shut-off valve 14, which, as shown, can be designed as a solenoid valve, to the hydraulic accumulators 12. From line 9, a line 15 leads to the shut-off valve 14 On the other hand, the shut-off valve 14 is via a return line 16 via an orifice 17 and a filter 18, through which the return line 10 can also be guided, to the oil reservoir 11. It can be seen that the shut-off valve 14 must have two positions. In the position shown, the four connected lines 13, 15, 13, 16 are each terminated.
  • the two parts of the connecting line 13 are connected to one another and, on the other hand, the line 15 is connected to the return line 16.
  • the latter position corresponds to the stage when the damping system is switched on, that is to say the hydraulic accumulators 12 are connected to the main line 1 and thus to the hydraulic cylinders 3 via the connecting line 13.
  • the shut-off valve 14 can be operated manually, in which case a safety valve should be provided in the connecting line 13 to protect the hydraulic accumulators 12 against overload.
  • a safety valve as shown, can be dispensed with.
  • the control valve 2 and the shut-off valve 14 are bridged via a filling line 19, 20.
  • the filling line 19 branches off from the main line 1 upstream of the switching valve 2 and leads to a pressure reducing valve 21 which, according to the symbols shown, is designed as a controlled pressure limiting valve.
  • the second part or the filling line 20 leads from the pressure reducing valve 21 to the hydraulic accumulators 12 via a check valve 22.
  • a return line 23 connects the pressure reducing valve 21 to the oil reservoir 11.
  • the pressure reducing valve 21 is designed such that it is open at low pressures in the filling line 19, that is to say connects the filling lines 19 and 20 to one another.
  • the pressure reducing valve 21 is set to a limit pressure which corresponds to the desired boost pressure in the hydraulic accumulators 12 and which corresponds approximately to the expected pressure when the loading shovel is raised in the main line 1. If this set limit pressure is reached and exceeded, the pressure reducing valve 21 closes the filling line 20 and excess oil or leak oil can flow back into the oil reservoir 11 via the return line 23.
  • the check valve 22 ensures that the set and desired boost pressure is stored and maintained in the hydraulic accumulators 12.
  • a filling process of the loading shovel proceeds as follows: First of all, the continuously driven pressure source conveys hydraulic medium without any significant overpressure in circulation, whereby the individual components, valves and the like. Like., Are set as shown in Figure 1.
  • the shut-off valve 14 is closed.
  • the control valve 2 is in its illustrated starting position and the pressure reducing valve 21 is open. Since there is no significant pressure in the filling line 19, the hydraulic accumulators 12 are only loaded with their preload pressure.
  • the shut-off valve 14 may be controlled depending on the driving speed. This control may be set and designed so that a certain speed limit of the order of 6 km / h can only be reached in second gear.
  • the pressure in the filling line 19 and via the opened pressure reducing valve 21 in the filling line 20 and thus in the hydraulic accumulators 12 also increases.
  • the hydraulic accumulators 12 are charged to a desired boost pressure, which is limited by the setting of the pressure reducing valve 21.
  • the set boost pressure can be in the order of 100 to 120 bar.
  • the pressure reducing valve 21 switches over, so that the hydraulic accumulators 12 are protected against this increased pressure even as the pressure in the filling line 19 increases.
  • the control valve 2 is switched accordingly, as a result of which the part of the main line 1 between the control valve 2 and the hydraulic cylinders 3 is shut off.
  • a pressure will build up, which is referred to as the carrying pressure and the weight of the Loading shovel and the picked up goods corresponds.
  • This carrying pressure can also be of the order of magnitude of 100 to 120 bar and is dependent on the degree of filling of the loading shovel and the specific weight of the load as well as other factors. However, its fluctuations are relatively small. If the wheel loader starts moving in the sense of a driving process, then when a certain driving speed is exceeded, for example 6 km / h, the set switching point of the shut-off valve 14 is exceeded in the second gear, so that it switches to its other position shown in FIG. 1.
  • the hydraulic accumulators 12 are released from the included boost pressure to the preload pressure while the wheel loader is returning from the unloading point to the charging point when the set driving speed of 6 km / h is exceeded. It will So here the damping system is switched on, which is used for the conscious damping of pitching vibrations while driving. Since the loading weight is absent due to the dumped load, a comparatively low residual pressure will also occur in the hydraulic accumulators 12.
  • the shut-off valve 14 switches over again at the charging point or when the set driving speed is undershot and a new filling cycle can begin.
  • FIG. 2 shows only the section of the hydraulic system that is essential for the invention, which is otherwise unchanged from the configuration according to FIG. 1.
  • the filling line 19 does not branch off from the main line 1 here, but takes hydraulic medium from the oil reservoir 11.
  • a separate pump 24 is provided in the filling line 19.
  • the pressure reducing valve 21 is designed here as a two-position solenoid switching valve. It is controlled between its two positions shown by a pressure switch 25, which is set to a desired boost pressure in the filling line 20.
  • the pump 24 is actuated and the hydraulic accumulators 12 charged via the interconnected fill lines 19 and 20.
  • the pressure reducing valve 21 is designed as a pressure cutter. It has the two positions in which the fill lines 19 and 20 are either blocked off or connected to one another.
  • the pressure reducing valve 21 is controlled via the pressure switch 25 in accordance with the pressure prevailing in the filling line.
  • the filling line 19 is here connected to the main line 1 upstream of the control valve 2, as in the exemplary embodiment in FIG. Hydraulic medium is not returned to the reservoir 11 here.
  • the hydraulic system is protected by the pressure relief valve integrated in the control valve 2.
  • FIG. 4 shows an embodiment of the pressure reducing valve 21, which corresponds to that according to FIG. 1.
  • the circuit is also quite similar, with the one exception that the filling line 19 is not connected here to the main line 1 upstream of the control valve 2, but rather via part of the filling line 13 to the main line 1 downstream of the control valve 2. So u. U. not used the highest pressures occurring in the main line 1 for storing the boost pressure in the hydraulic accumulators 12; however, this circuit can be useful or desirable.
  • a throttle 26 can be assigned to the pressure reducing valve 21 or integrated therein. The throttle 26 can also be arranged in the filling line 19 or the filling line 20.
  • the throttle cross section can be adjustable in order to introduce a time dependency in this way, so that depending on the time different charging pressures can be stored in the hydraulic accumulators 12, which can correspond to different filling levels of a loading scoop, so that in this way an even better adaptation of the respective boost pressure to the respective carrying pressure in the hydraulic cylinders 3.
  • the pressure difference between the two pressures mentioned is thus even smaller. In extreme cases, any vertical movement of the loading shovel does not occur during a connection process via the shut-off valve 14.
EP90103203A 1989-03-21 1990-02-20 Hydraulikanlage für Baumaschinen, insbesondere für Radlader, Schlepper u. dgl. Expired - Lifetime EP0388641B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3909205A DE3909205C1 (es) 1989-03-21 1989-03-21
DE3909205 1989-03-21

Publications (3)

Publication Number Publication Date
EP0388641A2 EP0388641A2 (de) 1990-09-26
EP0388641A3 EP0388641A3 (de) 1991-06-05
EP0388641B1 true EP0388641B1 (de) 1993-04-28

Family

ID=6376831

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90103203A Expired - Lifetime EP0388641B1 (de) 1989-03-21 1990-02-20 Hydraulikanlage für Baumaschinen, insbesondere für Radlader, Schlepper u. dgl.

Country Status (5)

Country Link
EP (1) EP0388641B1 (es)
AT (1) ATE88773T1 (es)
DE (2) DE3909205C1 (es)
DK (1) DK0388641T3 (es)
ES (1) ES2041061T3 (es)

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DE10060430B4 (de) * 1999-12-16 2009-04-02 Caterpillar Inc., Peoria Hydraulisches Fahrsteuersystem
DE102021208932B3 (de) 2021-08-16 2022-12-29 Robert Bosch Gesellschaft mit beschränkter Haftung Stabilisierungsmodul

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ATE150508T1 (de) * 1991-09-04 1997-04-15 Orenstein & Koppel Ag Hydraulisches schwingungsdämpfungssystem für mit arbeitsgeräten versehene arbeitsmaschinen
DE4221943C2 (de) * 1991-09-04 1996-01-25 Orenstein & Koppel Ag Hydraulikanlage für mit Arbeitsgeräten versehene fahrbare Arbeitsmaschinen
DE4129509C2 (de) * 1991-09-05 1994-06-16 Rexroth Mannesmann Gmbh Hydraulische Steueranordnung für Baumaschinen
DE4231399A1 (de) * 1992-08-20 1994-02-24 Rexroth Mannesmann Gmbh Hydraulische Steuereinrichtung
DE4416228A1 (de) * 1994-05-07 1995-11-09 Rexroth Mannesmann Gmbh Hydraulische Anlage für ein mobiles Arbeitsgerät, insbesondere für einen Radlader
US5992146A (en) * 1996-04-12 1999-11-30 Caterpillar Inc. Variable rate ride control system
US5706657A (en) * 1996-04-12 1998-01-13 Caterpillar Inc. Ride control system with an auxiliary power source
DE19622762A1 (de) * 1996-06-07 1997-12-11 Rexroth Mannesmann Gmbh Nutzfahrzeug, insbesondere für die Landwirtschaft
SE9700297D0 (sv) * 1997-01-31 1997-01-31 Lars Bruun Anordning vid hydrauliskt manövrerade arbetsredskap
DE19711769C2 (de) 1997-03-21 1999-06-02 Mannesmann Rexroth Ag Hydraulische Steueranordnung für eine mobile Arbeitsmaschine insbesondere für einen Radlader
DE19734658A1 (de) * 1997-08-11 1999-02-18 Mannesmann Rexroth Ag Hydraulische Steueranordnung für eine mobile Arbeitsmaschine, insbesondere für einen Radlader
SE511039C2 (sv) 1997-09-30 1999-07-26 Volvo Wheel Loaders Ab Lastarmsfjädringssystem för dämpning av lastarmarsrörelse
DE19751357B4 (de) * 1997-11-20 2007-01-25 Bosch Rexroth Aktiengesellschaft Hydraulische Steueranordnung für eine mobile Arbeitsmaschine, insbesondere für einen Radlader, zur Dämpfung von Nickschwingungen
DE19754828C2 (de) * 1997-12-10 1999-10-07 Mannesmann Rexroth Ag Hydraulische Steueranordnung für eine mobile Arbeitsmaschine, insbesondere für einen Radlader, zur Dämpfung von Nickschwingungen
DE19913784A1 (de) 1999-03-26 2000-09-28 Mannesmann Rexroth Ag Lastfühlende hydraulische Steueranordnung für eine mobile Arbeitsmaschine
WO2001086153A1 (de) * 2000-05-11 2001-11-15 Mannesmann Rexroth Ag Hydraulische steueranordnung
GB2365407B (en) 2000-05-25 2003-10-08 Bamford Excavators Ltd Hydraulic system for wheeled loader
US7204086B2 (en) 2000-05-25 2007-04-17 J.C Bamford Excavators Limited Method of operating a hydraulic system for a loader machine
DE10127486A1 (de) * 2001-06-07 2002-12-12 Claas Selbstfahr Erntemasch Entlastungsvorrichtung für eine Hubeinrichtung
DE10148962C1 (de) * 2001-10-04 2003-02-27 Hydac Technology Gmbh Steuervorrichtung
DE102004033890A1 (de) * 2004-07-13 2006-02-16 Bosch Rexroth Aktiengesellschaft Hydraulische Steueranordnung
DE102008043845A1 (de) * 2008-11-19 2010-05-20 Deere & Company, Moline Fahrzeug mit Ladevorrichtung
CN102587444B (zh) * 2012-03-07 2014-07-30 浙江大学 一种具有能量差动回收的挖掘机油液混合动力系统
DE102018210471B3 (de) 2018-06-27 2019-09-05 Robert Bosch Gmbh Hubwerksfederung und Hubwerk

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Publication number Priority date Publication date Assignee Title
DE10060430B4 (de) * 1999-12-16 2009-04-02 Caterpillar Inc., Peoria Hydraulisches Fahrsteuersystem
DE102021208932B3 (de) 2021-08-16 2022-12-29 Robert Bosch Gesellschaft mit beschränkter Haftung Stabilisierungsmodul

Also Published As

Publication number Publication date
DK0388641T3 (da) 1993-09-27
DE3909205C1 (es) 1990-05-23
EP0388641A2 (de) 1990-09-26
EP0388641A3 (de) 1991-06-05
ATE88773T1 (de) 1993-05-15
ES2041061T3 (es) 1993-11-01
DE59001284D1 (de) 1993-06-03

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