EP4162161A1 - Procédé pour adapter une pression d'une pompe hydraulique d'un système d'entraînement - Google Patents

Procédé pour adapter une pression d'une pompe hydraulique d'un système d'entraînement

Info

Publication number
EP4162161A1
EP4162161A1 EP21730532.5A EP21730532A EP4162161A1 EP 4162161 A1 EP4162161 A1 EP 4162161A1 EP 21730532 A EP21730532 A EP 21730532A EP 4162161 A1 EP4162161 A1 EP 4162161A1
Authority
EP
European Patent Office
Prior art keywords
pressure
hydraulic pump
max
pump
maximum
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.)
Pending
Application number
EP21730532.5A
Other languages
German (de)
English (en)
Inventor
Ronny Herrmann
Matthias Mueller
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP4162161A1 publication Critical patent/EP4162161A1/fr
Pending legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/002—Hydraulic systems to change the pump delivery
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/26—Control
    • F04B1/28—Control of machines or pumps with stationary cylinders
    • F04B1/29—Control of machines or pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B1/295—Control of machines or pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2205/00—Fluid parameters
    • F04B2205/18—Pressure in a control cylinder/piston unit

Definitions

  • the invention relates to a method for adapting a pressure of a hydraulic pump of a travel drive, preferably a method for learning a parameter of a pump characteristic or a pump characteristic curve or a computation rule for adapting a pressure of a hydraulic pump of a travel drive.
  • hydrostatic travel drives for mobile work machines in which a hydraulic pump and one or more hydraulic motors are connected to one another in a closed hydraulic circuit.
  • the hydraulic pump is driven by an internal combustion engine - e.g. a diesel engine - and the hydraulic motors ultimately drive the mobile work machine - e.g. via a respective wheel.
  • the hydraulic pump of such travel drives is often adjustable in terms of its delivery volume.
  • Hydrostatic axial piston pumps are used, among other things, in travel drives for construction machinery.
  • a partial function of these pumps is to limit the maximum allowable pressure. This is necessary, among other things, to limit torques and to limit the maximum permissible pressures of the components.
  • hydromechanical pressure control valves are also used. These valves limit the high pressure by reducing the control pressure of the pump and thereby reducing the pump's displacement. If the pump is electronically controlled, “closed loop” pressure regulators or controlled solutions that are calibrated are sometimes used, as disclosed in patent application DE 10 2018210685 A1.
  • the respective methods have several disadvantages.
  • the pressure relief valve causes high losses and subsequent thermal loads, which corresponds to additional costs.
  • a pressure relief valve can only be used to set a fixed pressure
  • the hydraulic mechanical pressure cut-off controller generates additional costs, especially when there is electrical control, and is temperature-dependent and is subject to tolerances and drift behavior.
  • the design for highly dynamic and stable behavior is very complex and only a fixed pressure can be specified.
  • the electronically controlled solutions with calibration are temperature-dependent and are subject to tolerances and drift behavior and only a fixed pressure can be specified.
  • the electronic "closed loop" controller disclosed in DE 102018210685 A1 has the following disadvantages:
  • the invention is based on the object of producing a method which eliminates the above-mentioned disadvantages.
  • a method for adapting a pressure of a hydraulic pump of a travel drive wherein the travel drive is provided with the hydraulic pump, which is coupled to a drive machine, for supplying pressure medium to a hydraulic motor of the travel drive that can be coupled to an output Actuating cylinder with at least one cylinder space and an adjustable stroke volume via it and at least one electrically controllable pressure valve is provided, via which the cylinder chamber can be acted upon with an adjusting pressure, and with a device via which a pressure of the hydraulic pump can be regulated by influencing the setting pressure, the pressure being controllable, the method comprising the following steps: a) Calculation a maximum permissible control pressure taking into account the stroke volume of the hydraulic pump or a variable representing this stroke volume, the rotational speed of the hydraulic pump and a maximum permissible pressure of the hydraulic pump; b) acquisition of the current pressure of the hydraulic pump; c) comparison of the current pressure of the hydraulic pump with the maximum allowable pressure; d) Correction of the maximum
  • a method for adapting a pressure of a hydraulic pump of a traction drive is provided, the traction drive being provided with the hydraulic pump for supplying pressure medium to a hydraulic motor of the traction drive that can be coupled to an output, the pressure generated by the hydraulic pump being controllable by influencing a setting pressure
  • the method comprises the following steps: a) calculating a maximum permissible control pressure taking into account a stroke volume of the hydraulic pump or a variable representing this stroke volume, the rotational speed of the hydraulic pump and a maximum permissible pressure of the hydraulic pump; b) detecting the currently generated pressure of the hydraulic pump; c) comparing the currently generated pressure of the hydraulic pump with the maximum permissible pressure; and d) adapting the set pressure taking into account the difference between the current pressure of the hydraulic pump and the maximum permissible pressure by correcting a learning factor, which is preferably a parameter of a pump characteristic or a pump characteristic curve or a calculation rule.
  • This solution is particularly advantageous because it can always adapt the behavior of the hydraulic pump by correcting the learning factor.
  • the reason for this is that the set pressure can be calculated taking into account the learning factor that was corrected in the previous cycle.
  • a method is provided, wherein the learning factor in step d. is taught.
  • a method is provided, the method further comprising the following step: e) comparing the maximum permissible control pressure that was established in step d. was adapted, with the control pressure, which was calculated taking into account a driver's request and independently of the maximum permissible pressure of the hydraulic pump; f) Control of the hydraulic pump with the smaller value between the control pressure, which was calculated taking into account a driver's request and independently of the maximum allowable pressure of the hydraulic pump, and the maximum allowable control pressure.
  • a method is provided, wherein it is checked between steps b and c whether predetermined conditions are met; wherein step c. is carried out if the specified conditions are met.
  • a method is provided, one of the predetermined conditions being that the absolute value of the difference between the current pressure of the hydraulic pump and the maximum permissible pressure is greater than a predetermined value.
  • a method is provided, one of the specified conditions being that the absolute value of the difference between the current pressure of the hydraulic pump and the maximum permissible pressure for a specified time window is greater than a specified value.
  • a method is provided, wherein in step e. the learning factor is corrected multiplicatively or additively.
  • a method is provided, wherein if the current pressure of the hydraulic pump is higher than the maximum permissible pressure, during said step d. the learning factor is corrected downwards.
  • a method is provided, wherein if the current pressure of the hydraulic pump is less than the maximum permissible pressure and preferably other conditions are active (e.g. that the limitation is below control values of the driver's request), during said step d. the learning factor is corrected upwards.
  • a method is provided, wherein, if the current pressure of the hydraulic pump is less than the maximum permissible pressure and the maximum permissible control pressure is less than the control pressure, which takes into account a driver's request and regardless of the maximum permissible pressure of the Hydraulic pump was calculated during said step d. the learning factor is corrected upwards.
  • a method is provided, wherein the learning factor is reset during a vehicle calibration.
  • a method is provided, wherein if the difference between the learning factor before and after the correction is greater than a predetermined value, a diagnostic message is generated.
  • a method is provided, wherein in step d. the currently generated and recorded pressure is filtered to take the pressure dynamics into account.
  • a method is provided, wherein the maximum permissible pressure of the hydraulic pump is different for pulling and towing or braking operation.
  • Fig. 1 shows a hydraulic circuit diagram of a hydrostatic drive according to the prior art
  • FIG. 2 shows characteristics of the hydrostatic travel drive according to FIG. 1,
  • FIG. 3 shows a more detailed block diagram of a method for controlling the hydrostatic travel drive of the method according to the prior art
  • FIG. 4 shows a simple block diagram of a method for adapting a pressure of a hydraulic pump of a travel drive according to an exemplary embodiment of the present invention.
  • a hydrostatic travel drive 1 has a hydraulic pump 2 which is fluidically connected in a closed hydraulic circuit via the working lines 4 and 6 to a hydraulic motor, not shown, for its pressure medium supply.
  • the hydraulic pump 2 is coupled to a drive machine (not shown) via a drive shaft 8 for the transmission of a torque.
  • the coupling is not translated, so that the speed of the drive machine and the hydraulic pump 2 are identical.
  • the hydraulic pump 2 is designed as an axial piston pump with a swash plate design and can be operated in both directions of rotation and in both pump and motor operation. It has an adjustable displacement volume VP and an adjusting device 10 designed as a double-acting hydraulic cylinder.
  • the hydraulic cylinder 10 has a first cylinder chamber 12 and a second cylinder chamber 14 counteracting the first.
  • the first cylinder chamber 12 is connected to the output of a first pressure reducing valve 18 via a first control pressure line 16.
  • the latter is connected to a control pressure line 20, which can be supplied with control pressure medium via a control pressure connection ps and via a feed pump 22, which sits on the same drive shaft 8 as the hydraulic pump 2.
  • the second cylinder chamber 14 is connected via a second control pressure line 24 to a second pressure reducing valve 26, which is connected to the control pressure line 20.
  • the pressure reducing valves 18, 26 can be actuated electromagnetically, the respective setting pressure p a or p b resulting in the setting pressure line 16 or 24 being proportional to a control current I a or I b of the electromagnet a or b according to a valve characteristic.
  • the set pressures p a , p b of the cylinder chambers 12, 14 can thus be controlled via the electromagnetic actuation of the pressure reducing valves 18, 26 by specifying the control currents I a , I b.
  • the electromagnets a, b of the pressure reducing valves 18, 26 are signal-connected to an electronic control unit 32 via a respective signal line 28 and 30, respectively.
  • the hydrostatic travel drive 1 has a speed detection unit 34 via which a speed np of the hydraulic pump 2 can be detected and transmitted to the electronic control unit 32 via a signal line 36.
  • the travel drive 1 also has a speed detection unit (not shown) via which the speed PM of the hydraulic motor can be detected and transmitted to the electronic control unit 32 via the signal line 38.
  • the hydrostatic travel drive 1 has a pressure limiting valve 40 which is connected to the respective working line 4, 6. Both pressure limiting valves 40 have their outputs connected to a feed pressure line 44 which is connected to the feed pump 22.
  • the feed pressure line 44 is fluidically connected to the control pressure line 20 via a throttle 42.
  • pressure relief valves 40 each have a feed or suction function in the form of a check valve.
  • the hydrostatic travel drive 1 can be operated both in pulling mode and in towing or braking mode.
  • the hydraulic pump 2 works in pump mode, in braking mode it works in motor mode.
  • the direction of travel can be reversed while the direction of rotation of the drive shaft 8 and the drive machine (diesel engine) remain the same.
  • the electronic control unit 32 is connected via a signal line 46 to an operator interface in the form of an accelerator pedal (not shown).
  • a driver transmits a speed request to the electronic control unit 32 via the accelerator pedal. This can affect both reverse and forward travel. If the accelerator pedal is actuated, this corresponds to the pulling or pumping operation of the hydraulic pump 2; if the accelerator pedal, on the other hand, is withdrawn, this corresponds to the braking or motoring of the hydraulic pump 2 Hydraulic pump 2.
  • the control unit is designed in such a way that it can determine the corresponding operation on the basis of said actuation.
  • the hydrostatic travel drive 1 also has an actuatable travel direction switch (not shown), which is signal-connected to the electronic control unit 32 via a signal line 48.
  • the hydraulic pump 2 is controlled in its reversed or non-reversed adjustment range, i.e. on this side or on the other side of the neutral position of the stroke volume of the hydraulic pump 2.
  • the following driving states are defined:
  • Forward travel, braking operation pressurization of the second cylinder chamber 14 via the second setting pressure line 24 and the second pressure reducing valve 26 with the second setting pressure Pb by controlling the second pressure reducing valve 26 with the control current lb via the control unit 32 via the signal line 30.
  • Reverse travel, pulling operation pressurization of the second cylinder chamber 14 via the chain 24, 26, 30, 32.
  • Reverse travel, braking operation pressurization of the first cylinder chamber 12 via the chain 16, 18, 28, 32.
  • the hydraulic pump 2 is designed in such a way that the pressure p, which is present in the high-pressure one of the working lines 4, 6, counteracts the then effective control pressure p a or p b and is effective in the direction of its own reduction.
  • the hydraulic pump 2 has a constructively implemented control loop.
  • the hydraulic pump 2 configured as an axial piston pump in swash plate design, this is implemented in such a way that a control disc of the hydraulic pump 2 is arranged in a twisted manner with respect to an axis of rotation of its cylinder drum.
  • Mouths of those cylinders which are connected to the pressure kidney control disk, which has the pressure (high pressure), are thus arranged so as to be distributed asymmetrically with respect to a pivot axis of the swashplate.
  • the end sections of the working pistons guided in the cylinders, which are supported on the swash plate, are then also distributed asymmetrically.
  • the asymmetrically acting supporting forces of the working pistons result in a moment on the swash plate that swings back in pump operation and swings out in motor operation.
  • FIG. 2 shows a characteristic of the hydraulic pump 2 with open-loop control, that is to say with a directly controlled displacement or stroke volume VP.
  • the pressure p more precisely the pressure difference Dr between the working lines 4, 6, is plotted as a function of the displacement volume VP.
  • the first control pressure p a of the first cylinder chamber 12 is plotted as a parameter. This increases starting from the origin 0/0.
  • the nominal output of the diesel drive machine P nomen is shown as a dashed curve as the limiting output.
  • the starting point of the description is an unactuated accelerator or accelerator pedal and a prime mover rotating at idle speed.
  • a control signal or control current I a for the hydraulic pump 2, more precisely for its first pressure reducing valve 18, takes place via the electronic control unit 32 as a function of the speed of the diesel engine.
  • the first control pressure p a is increased in accordance with a characteristic map of the hydraulic pump 2 stored in the electronic control unit 32 according to FIG. Since there is still no load acting, the hydraulic pump 2 swings out fully to its maximum stroke volume Vp max and delivers its maximum volume flow Qmax at the rated speed.
  • a pressure or load pressure p for example 250 bar
  • p is established as a result of driving resistance. This process is symbolized in FIG. 2 by the arrow labeled with the number 2.
  • a point Q is then reached which lies on the curve P nomen.
  • the first control pressure p a at the nominal speed is dimensioned such that the hydraulic power pQmax of the hydraulic pump 2 corresponds to the nominal power P nomen.
  • the pressure p increases. Due to the aforementioned configuration of the hydraulic pump 2, in which the operating pressure p counteracts the first control pressure p a in the pulling operation of the hydraulic pump 2 in forward travel in the direction of a reduction in the stroke volume VP, the pressure p swivels the swivel cradle of the hydraulic pump 2 back, which slows down the journey .
  • the first control pressure p a is not changed during this and corresponds to the straight line (arrow 3) intersecting the point Q and representing the reduction in the stroke volume VP and the simultaneous increase in the pressure p or the pressure difference Dr.
  • control unit 32 intervenes in accordance with the pressure cut-off according to the invention and takes back the first set pressure p a .
  • the maximum permissible pressure p max can be prevented from being exceeded even if the load continues to increase.
  • the input variables of the method are the determined or estimated stroke volume VP or the corresponding swivel angle ap of the hydraulic pump 2, its speed np, and a predetermined limit of the pressure or working pressure p max , in this case 450 bar.
  • a pump characteristic or pump characteristic curve or arithmetic rule 82 for operating the hydraulic pump 2 in pulling mode (pump mode) and 84 for braking or motoring the hydraulic pump 2 is stored in the electronic control unit 32 for each pressure limit p max.
  • the respective control pressure p a or p b is described as a function of the pump speed np and the pump swivel angle ap (in percent of the maximum swivel angle).
  • the set pressures p a and p b are also shown as a percentage of the maximum control or set pressure p smax available in the control pressure line 20.
  • the scale of the second control pressure p b provided for the second control chamber 14 during engine operation extends from zero to -50%.
  • the plus and minus signs represent the different effective directions of the pressure due to the opposing actuating chambers 12, 14.
  • the maximum permissible control pressure p amax for traction operation and p b ax for braking operation is first determined in accordance with method 52. This takes place permanently anew with a fixed limit p max , since ap in particular changes during operation due to its load dependency.
  • a requested first set pressure p a68 which results from the actuation of the accelerator pedal 68 according to FIG. 1, is then compared.
  • the latter Control pressure and the ascertained maximum permissible first control pressure p amax are compared by control unit 32, and the lower one is selected in step 86.
  • step 88 With the maximum permissible second control pressure p bmax .
  • the smaller of the set pressures selected in each case from steps 86 and 88 is then multiplied again by the maximum available control pressure p sm ax, which results in a real set pressure p a or p b from the set pressure previously specified in percent.
  • This is included in a respective valve characteristic curve 90 or 92 for the pressure reducing valve 18 or 26, from which the associated control current I a or I b for controlling the pressure reducing valve 18 or 26 is determined.
  • the control pressures p a, P b required in normal ferry operation and the maximum permissible set pressures p am ax, Pbmax are determined, the smaller of which leads to the control current l a , l b . If the control pressure p a68 output in accordance with the driver's request is above the limit p ama x or pbmax, the control current p a or pb is limited or cut off.
  • the design for highly dynamic and stable behavior is very complex.
  • the present invention will make it possible to compensate for the tolerances, the fluctuations in the control behavior over temperature and aging behavior, and to dynamically adapt the permissible maximum pressures.
  • FIG. 4 shows a method according to an embodiment of the present invention which overcomes the problems mentioned above.
  • the pump characteristic or the pump characteristic or the arithmetic rule depends on a learning factor that is a parameter of the performance characteristics.
  • the learning factor can be applied both multiplicatively and additively to the performance curve so that the performance curves can be corrected upwards or downwards.
  • the first step 101 is analogous to that shown in Figure 3 step 52. More specifically, np depending on the current values ap and p ma x of the operating state of the traveling mechanism, first the respective maximum permissible operating pressure p a ax for the train operations and Pbmax for the braking operation determined. In the following step 102, the pressure difference Dr between the working lines 4, 6 is detected.
  • the currently generated and recorded pressure p is preferably filtered in order to take the pressure dynamics into account and to neglect the fluctuations.
  • the currently generated pressure p of the hydraulic pump 2 is greater or less than the maximum permissible pressure p max , there is an indication that the performance characteristics should be corrected (either because the currently generated pressure p is too high or because it is too low ). It is therefore possible that the determined maximum permissible control pressure P amax for pulling operation and p bmax for braking operation have to be corrected.
  • the first condition is that the deviating from the maximum allowable pressure p ma x generated pressure p is undesirable. In other words, explains, it must be verified that the reason why the pressure generated by the pump P from the maximum pressure p ma x is different, is not at the request of the driver, but in the performance characteristics by which the maximum allowable control pressure p a ax for train operation and pbmax for braking operation have been calculated in step 101.
  • the learning factor is corrected upwards or downwards and the learning factor is preferably learned so that this correction of the performance characteristics can be saved.
  • the learning factors are permanently stored in the control unit so that the learned factors are already available when the system is restarted.
  • Additional conditions can be:
  • the maximum permissible signal pressure p a ax for train operation and p bmax for braking operation are recalculated on the basis of the new learning factor.
  • the set pressures p a ax and pbmax are then multiplied by the maximum available control pressure p sm ax, which results in a real set pressure p ama x or pbmax from the set pressure given in percent up to that point.
  • steps 103 and 104 without consideration of the maximum pressure p ma x, taking into account the depression of the accelerator are in parallel with steps 101 and 102, first, 68 the actuating pressures p a and p b in percent of the maximum standing in the control pressure line 20 provided Control or control pressure p sm ax is calculated (step 103). The set pressures p a and pb are then multiplied by the maximum available control pressure p sm ax, which results in a real set pressure p a or p b from the set pressure previously specified in percent. In step 105, the values of the set pressures from steps 102 and 104 are compared and the minimum value for the set pressures is taken.
  • step 106 these values are included in the respective valve characteristic curve 90 or 92 for the pressure reducing valve 18 or 26, from which the associated control current I a or I b for controlling the pressure reducing valve 18 or 26 is determined.
  • the method described with reference to FIG. 4 can always be active in ferry operation and can itself recognize the driving states in which learning is allowed.
  • the algorithm adapts too low and too high pressures in pushing (negative pressures) as well as in pulling mode (positive pressures).
  • the learning factor can be reset during vehicle calibration and corrected and learned again during ferry operation.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Fluid Gearings (AREA)
  • Control Of Positive-Displacement Pumps (AREA)

Abstract

L'invention concerne un procédé pour adapter une pression (p) d'une pompe hydraulique (2) d'un système d'entraînement (1), ce système d'entraînement étant équipé de la pompe hydraulique (2) pour alimenter en fluide sous pression un moteur hydraulique (78) du système d'entraînement (1) pouvant être accouplé à une sortie (80), la pression (p) générée par la pompe hydraulique (2) pouvant être régulée sous l'influence d'une pression de réglage (pa, pb), le procédé comprenant les étapes qui consistent : a. à calculer une pression de réglage maximale admissible (pamax, pbmax) avec prise en compte d'un volume de déplacement (VP) de la pompe hydraulique (2) ou d'une grandeur (αP) représentant ce volume de déplacement (VP), de la vitesse de rotation (nP) de la pompe hydraulique (2) et d'une pression maximale admissible (pmax) de la pompe hydraulique (2); b. à détecter la pression (p) générée dans l'instant de la pompe hydraulique (2); c) à comparer la pression (p) générée dans l'instant de la pompe hydraulique (2) avec la pression maximale admissible (pmax); et d. à adapter la pression de réglage maximale admissible (pamax, pbmax) avec prise en compte de la différence entre la pression (p) dans l'instant de la pompe hydraulique (2) et la pression maximale admissible (pmax), un facteur d'apprentissage qui est un paramètre d'une caractéristique de pompe ou d'une courbe caractéristique de pompe ou d'une règle de calcul étant corrigé.
EP21730532.5A 2020-06-04 2021-05-31 Procédé pour adapter une pression d'une pompe hydraulique d'un système d'entraînement Pending EP4162161A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102020206968.9A DE102020206968A1 (de) 2020-06-04 2020-06-04 Verfahren zur adaption eines drucks einer hydropumpe eines fahrantriebes
PCT/EP2021/064477 WO2021244999A1 (fr) 2020-06-04 2021-05-31 Procédé pour adapter une pression d'une pompe hydraulique d'un système d'entraînement

Publications (1)

Publication Number Publication Date
EP4162161A1 true EP4162161A1 (fr) 2023-04-12

Family

ID=76305904

Family Applications (1)

Application Number Title Priority Date Filing Date
EP21730532.5A Pending EP4162161A1 (fr) 2020-06-04 2021-05-31 Procédé pour adapter une pression d'une pompe hydraulique d'un système d'entraînement

Country Status (4)

Country Link
EP (1) EP4162161A1 (fr)
CN (1) CN115667714A (fr)
DE (1) DE102020206968A1 (fr)
WO (1) WO2021244999A1 (fr)

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3867458D1 (de) * 1988-01-14 1992-02-13 Hydromatik Gmbh Automotive antriebseinrichtung fuer maschinen und fahrzeuge.
US5249422A (en) * 1991-12-20 1993-10-05 Caterpillar Inc. Apparatus for calibrating the speed of hydrostatically driven traction motors
US8024925B2 (en) 2005-11-08 2011-09-27 Caterpillar Inc. Apparatus, system, and method for controlling a desired torque output
DE102006055932A1 (de) * 2006-11-27 2008-05-29 Robert Bosch Gmbh Verfahren zur Regelung einer Hydropumpe und elektronische Steuereinheit
CN101680542B (zh) 2007-03-30 2014-07-23 株式会社小松制作所 具备静液压式无级变速器的车辆的控制装置
DE102018210685A1 (de) 2018-06-29 2020-01-02 Robert Bosch Gmbh Hydrostatischer Fahrantrieb und Verfahren zur Steuerung des hydrostatischen Fahrantriebes
DE102018210694A1 (de) * 2018-06-29 2020-01-02 Robert Bosch Gmbh Hydrostatische Axialkolbenpumpe für einen hydrostatischen Fahrantrieb
DE102018216750A1 (de) 2018-09-28 2020-04-02 Robert Bosch Gmbh Verfahren zur Steuerung einer Axialkolbenpumpe und Antriebseinheit mit einer derartigen Axialkolbenpumpe und hydrostatischer Fahrantrieb mit einer derartigen Antriebseinheit

Also Published As

Publication number Publication date
DE102020206968A1 (de) 2021-12-23
WO2021244999A1 (fr) 2021-12-09
CN115667714A (zh) 2023-01-31

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