WO2015082116A1 - Mécanisme d'entraînement hydrostatique et procédé pour faire fonctionner un tel mécanisme - Google Patents

Mécanisme d'entraînement hydrostatique et procédé pour faire fonctionner un tel mécanisme Download PDF

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Publication number
WO2015082116A1
WO2015082116A1 PCT/EP2014/072446 EP2014072446W WO2015082116A1 WO 2015082116 A1 WO2015082116 A1 WO 2015082116A1 EP 2014072446 W EP2014072446 W EP 2014072446W WO 2015082116 A1 WO2015082116 A1 WO 2015082116A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
pressure
main flow
hydrostatic drive
main
Prior art date
Application number
PCT/EP2014/072446
Other languages
German (de)
English (en)
Inventor
Matthias Greiner
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 WO2015082116A1 publication Critical patent/WO2015082116A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/38—Control of exclusively fluid gearing
    • F16H61/40—Control of exclusively fluid gearing hydrostatic
    • F16H61/4078—Fluid exchange between hydrostatic circuits and external sources or consumers
    • F16H61/4096—Fluid exchange between hydrostatic circuits and external sources or consumers with pressure accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/38—Control of exclusively fluid gearing
    • F16H61/40—Control of exclusively fluid gearing hydrostatic
    • F16H61/4008—Control of circuit pressure
    • F16H61/4017—Control of high pressure, e.g. avoiding excess pressure by a relief valve

Definitions

  • the invention relates to a hydrostatic drive with at least one Hydrostaten having an output which is connected to a high-pressure region comprising a high pressure accumulator, and with a check valve means between the output of the hydrostatic and the high-pressure accumulator.
  • the invention further relates to a method for operating such a hydrostatic drive.
  • the hydrostatic drive can be used, for example, to represent a hydraulic hybrid powertrain of a motor vehicle.
  • a hydraulic hybrid powertrain for example, at least one hydraulic machine, which is also referred to as hydrostat, is connected to a first pressure port of a valve device.
  • a hydraulic pressure accumulator is connected to a second pressure port of the valve device.
  • the pressure in the hydraulic pressure accumulator that is to say at the second pressure connection, is greater than at an outlet of the hydraulic machine, that is to say the first pressure connection.
  • the reverse case is also possible.
  • the object of the invention is to provide the functionality of a hydrostatic drive with at least one hydrostats having an output which is connected to a high-pressure region comprising a high-pressure accumulator, and with a check valve device between the output of
  • the object is in a hydrostatic drive with at least one Hydrostaten having an output which is connected to a high-pressure region comprising a high pressure accumulator, and with a check valve means between the outlet of the hydrostatic and the high-pressure accumulator, achieved in that the check valve means includes two series-connected main flow valves, which are designed to represent a check valve function in opposite directions than normally closed main flow valves.
  • the main flow valves include, for example, a valve piston, which is also referred to as a main valve piston and is biased by at least one spring device into a closed position to illustrate the check valve function. Via a pressure connection of the main flow valve, the valve piston can be pressurized so that it opens against the biasing force of the spring device in the manner of a check valve.
  • a preferred embodiment of the hydrostatic drive is characterized in that the two main flow valves each have a first pressure port, which is normally closed by a main valve piston.
  • the main valve piston can be opened by a targeted pressure reduction in a control chamber by activating a pilot control valve for adjusting or regulating a fluid flow, which is also referred to as a main flow.
  • a further preferred embodiment of the hydrostatic drive is characterized in that in the main valve piston, a check valve is integrated.
  • the check valve closes, for example, a preferably throttled inlet opening in the control chamber.
  • the check valve integrated into the main valve piston improves the representation of the check valve function of the main valve piston.
  • a further preferred exemplary embodiment of the hydrostatic travel drive is characterized in that the two main flow valves are of the same design and interconnected with their first connections so that the closed main flow valves open when the pressure at the first pressure connection is greater than at a second pressure connection.
  • the two main flow valves are of the same design and interconnected with their first connections so that the closed main flow valves open when the pressure at the first pressure connection is greater than at a second pressure connection.
  • Pressure at the second pressure port is greater than at the first pressure port Enough.
  • the check valve function of the main flow valves allows a quick pressure equalization.
  • Pressure port is connected to the high pressure accumulator, with a second main flow valve is connected with its second pressure port to the high pressure area.
  • the second main flow valve is preferably connectable with its second pressure port to the outlet of the hydrostat.
  • the two first pressure ports of the two main flow valves are advantageously connected directly to each other.
  • Another preferred embodiment of the hydrostatic drive is characterized in that the two main flow valves each in the closed state, only a first sealing point between a
  • the inventive interconnection of the two main flow valves advantageously only two sealing points are required.
  • the control valve closing body belongs to a pilot valve, with which a control pressure is controlled in a control pressure chamber.
  • the pilot valve is advantageously integrated in the main flow valve.
  • the control pressure space is partially limited by the valve piston of the main valve, which is also referred to as the main valve piston.
  • a further preferred embodiment of the hydrostatic drive is characterized in that the two main flow valves are designed as 2/2-way valves with an open position and a closed position with non-return valve function. In the open position are the two
  • each main flow valve connected in both directions.
  • the main flow valves are opened, for example, by electromagnetic control.
  • In the closed position of the main flow valve a connection between the second and the first pressure connection is interrupted. With the check valve function is at an overpressure on the first
  • Pressure port allows opening of the valve piston of the main valve.
  • the invention further relates to a method for operating a previously described hydrostatic drive.
  • the combination according to the invention of the two main flow valves particularly advantageously allows a high functionality in the entire viscosity range.
  • the main flow valves are advantageously designed so that they switch properly even in the cold.
  • a preferred embodiment of the method is characterized in that a main flow valve connected to the high-pressure accumulator is actuated in order to release a fluid connection from the high-pressure accumulator into the high-pressure region.
  • a main flow valve connected to the high-pressure accumulator By controlling the main flow valve connected to the high-pressure accumulator, it is achieved that fluid flows from the high-pressure accumulator into the high-pressure region.
  • a main flow valve connected to the high-pressure area can be activated.
  • a further preferred exemplary embodiment of the method is characterized in that a main flow valve connected to the high-pressure region is activated in order to release a fluid connection from the high-pressure region into the high-pressure accumulator.
  • a main flow valve connected to the high-pressure region By controlling the main flow valve connected to the high-pressure region, it is achieved that fluid flows from the high-pressure region into the high-pressure accumulator in order to charge it. Therefore, this state is also referred to as a storage state of charge.
  • additionally connected to the high-pressure accumulator main flow valve can be controlled.
  • Figure 1 is a simplified hydraulic circuit diagram of a hydrostatic drive according to the invention and Figure 2 shows an embodiment of a valve device in longitudinal section, which represents two main flow valves in the hydraulic circuit diagram of Figure 1.
  • the hydrostatic travel drive 1 can be used, for example, in a hydraulic hybrid powertrain, which comprises a hydraulic drive in addition to an internal combustion engine drive.
  • the internal combustion engine drive is designed, for example, as an internal combustion engine and is also referred to as an internal combustion engine.
  • the hydraulic drive 1 comprises, for example, two hydraulic machines 3, 4, which are also referred to as hydrostats.
  • the two hydrostats 3, 4 or hydraulic machines can be operated advantageously both as a hydraulic pump and as a hydraulic motor.
  • the two hydraulic machines can be designed, for example, as hydraulic axial piston machines.
  • the two hydraulic machines can generally also be referred to as fluid machines and are indicated in FIG. 1 only by two rectangles 5 and 6.
  • the rectangles 5 and 6 are arranged within dashed rectangles 3 and 4, which indicate the hydrostat.
  • the two fluid machines or hydraulic machines 5 and 6 are hydraulically connected or connected to one another via the hydraulic system shown in FIG.
  • the hydraulic system comprises a high-pressure accumulator 8 and a low-pressure accumulator 9 for hydraulic medium, such as hydraulic oil.
  • the high-pressure accumulator 8, the low-pressure accumulator 9 and the two hydrostats 3, 4 or fluid machines 5, 6 are connected to a valve device 10 indicated only by an oblong rectangle.
  • a region 14 between the high-pressure accumulator 8 and the valve device 10 is subjected to a relatively high pressure, which is also referred to as high pressure. Therefore, the region 14 is also referred to as the high-pressure region 14.
  • a region 15 between the low-pressure accumulator 9 and the valve device 10 is referred to as a low-pressure region 15.
  • a check valve device 17 is connected between the high-pressure accumulator 8 and the valve device 10.
  • the check valve device 17 according to an essential aspect of the invention comprises two series-connected main flow valves 18 and 19.
  • the two main flow valves 18, 19 are designed as normally closed main flow valves.
  • Figure 1 is symbolically indicated that the two main flow valves 18, 19 are designed as 2/2-way valves with an open position and a closed position, which includes a check valve function.
  • the two main flow valves 18, 19 are electro-hydraulically controlled, for example by means of an electromagnet.
  • spring means By indicated spring means, the two main flow valves 18, 19 are biased in their illustrated closed positions with the check valve function.
  • the high pressure accumulator 8 is connected to a port A of the main flow valve 18, which is also referred to as the first main flow valve.
  • the valve device 10 is connected to a pressure port A of the main flow valve 19, which is also referred to as a second main flow valve.
  • the two main flow valves 18, 19 are hydraulically connected.
  • the check valve function of the main flow valves 18, 19 is symbolically indicated in Figure 1 by check valve balls.
  • the check valve balls close when the pressure at the pressure ports A is greater than at the pressure ports B. Accordingly, the check valve balls open when the pressure at the pressure ports B is greater than at the pressure ports A.
  • the two main flow valves 18, 19 in Figure 1 are the same. If the two main flow valves 18, 19 are controlled electro-hydraulically, then a flow connection in both directions between the pressure ports A and B is released.
  • 2 shows an embodiment of a valve device 21 is shown in longitudinal section.
  • the valve device 21 corresponds to an embodiment of the Main flow valves 18 and 19 in Figure 1.
  • the valve device 21 shown in Figure 2 which may also be referred to as the main flow valve, comprises a first pressure port 1 1, which corresponds to the pressure port B in Figure 1.
  • the valve device or the main flow valve 21 in Figure 2 further comprises a second pressure port 12, the pressure port A in
  • the valve device 21 shown in longitudinal section in Figure 2 comprises a main valve 22 and a pilot valve 23.
  • the valve device 21 further includes a valve housing 25 with the first pressure port 1 1 and the second pressure port 12th
  • the valve housing 25 comprises a housing body 26 and a
  • Housing body or pole tube body 27 The two housing body 26, 27 are pressure-tight. Between the two housing bodies 26, 27, a shim 28 is clamped, which limits a stroke of the main valve 22.
  • the main valve 22 includes a valve piston 30, also referred to as a main flow valve piston, which has a sealing surface at its lower end 31, which bears in a sealing manner on a sealing edge of the housing body 26 to depict a valve seat 32.
  • the valve seat 32 is closed.
  • Housing body 26 lifts, the valve seat 32 is opened.
  • the valve seat 32 (not shown), a direct connection between the two pressure ports 1 1 and 12 is released. This connection is interrupted when the valve seat 32 is closed.
  • the valve piston 30 is for the representation of the opening movement and the closing movement in the axial direction, that is in Figure 2 up and down, movable.
  • the term axial refers to a longitudinal axis 33 of the valve device 21.
  • the valve piston 30 has a through hole 34 extending in the radial direction, that is to say transversely to the longitudinal axis 33, which connects the second pressure port 12 to a control chamber 35 in the interior of the valve piston 30.
  • the through hole 34 represents a throttled control chamber inlet opening and is therefore also referred to as inlet throttle.
  • a through hole 37 extends in the axial direction through the valve piston 30 and constitutes a throttled control chamber drain opening. Therefore, the through hole 37 is also referred to as a drain throttle.
  • the through hole 37 is used to represent a valve seat 40 of the pilot valve 23.
  • the through hole 37 is closed by a check valve body, preferably in the form of a check ball, 41 in Figure 2 from below. Movement of the check valve body 41 downwards in FIG. 2 is limited by a sleeve 42.
  • the through-hole 37 in FIG. 2 is closed by a closing body 44.
  • the closing body 44 together with the through hole 37, constitutes the valve seat 40 of the pilot valve 23. Therefore, the closing body 44 is also referred to as a control valve closing body.
  • the closing body 44 is fastened to a lower end of a sealing element 45 of the pilot control valve 23 in FIG. 2, for example by means of a flared connection.
  • the sealing element 45 represents an anchor part 48 which is movable relative to an armature 50 in the axial direction limited.
  • the armature 50 is biased by an armature spring 52 in Figure 2 down.
  • armature spring 52 By the biasing force of the armature spring 52 of the coupled via the armature part 48 and the closing body 44 with the armature 50 valve piston 30 is moved to its closed position shown or held in the illustrated closed position when a the armature 50 associated solenoid 53 is not energized.
  • the closing body 44 is fastened.
  • the upper end of the anchor part 48 in FIG. 2 has a collar 54.
  • the anchor part 48 has a shoulder 55.
  • the anchor part 48 or the sealing element 45 is over a
  • Carrier device 60 coupled to the armature 50.
  • the entrainment device 60 is designed as a drive sleeve, with a first end 61, the in FIG 2 upper end, fixed to the armature 50 is connected.
  • a second end 62, the lower end in Figure 2 the driver 60 has radially inwardly bent entrainment claws, which represent a stop for the anchor member 48, in particular the paragraph 55 of the anchor member 48.
  • a spring device 64 is biased in the axial direction between the driving claws on the second end 62 of the driver 60 and the collar 54 of the anchor member 48 and sealing member 45.
  • the closing body 44 of the pilot valve 23 With a corresponding pressure difference between the second pressure port 12 and the first pressure port 1 1, the closing body 44 of the pilot valve 23 is held in its illustrated closed position. Due to the fixed connection between the closing body 44 and the anchor part 48, the anchor part 48 initially also remains in its illustrated closed position.
  • the driver 60 then moves together with the armature 50 against the biasing force of the spring means 64 in Figure 2 upwards until the second end 62 of the driver 60 abuts the shoulder 55 of the anchor member 48.
  • This movement of the armature 50 without the anchor portion 48 is also referred to as Ankerokweg.
  • Carrier device 60 that the anchor member 48 is moved upward, so that the closing body 44 is torn from the valve seat 40.
  • the associated opening in the outlet throttle 37 causes the valve piston of the main valve 22 opens.
  • the closing of the main valve 22 is interrupted by an interruption
  • the second main flow valve 19 is driven.
  • the first main flow valve 18 are driven. If medium from the high pressure accumulator 8 in the high pressure region to flow to the valve device 10, then the first main flow valve 18 is driven. If appropriate, the second main flow valve 19 can also be activated.
  • the first sealing point 71 is formed on the valve seat 32 between the main valve piston 30 and the housing body 26.
  • the second sealing point 72 is formed on the valve seat 40 between the control valve closing body 44 and the main valve piston 30.
  • the representation of the check valve function of the main flow valve 21 with only two sealing points 71 and 72 advantageously allows a robust operation over the entire viscosity range, even at low temperatures.
  • the hydrostatic drive 1 to maintain a pressure in the high-pressure accumulator 8 between the pressure connections A and B of the main flow valve 18, only the two sealing points (71 and 72 in FIG. 2) must be sealed.
  • the second main flow valve 19 does not have to seal.
  • Hydrostat 3, 4 to the high-pressure accumulator 8 has to seal only the second main flow valve 19 with its two sealing points between the pressure ports A and B.
  • the first main flow valve 18 must in the sealing of the
  • Hydrostat 3, 4 to the high-pressure accumulator 8 does not seal.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

L'invention concerne un mécanisme d'entraînement hydrostatique (1) comprenant au moins une structure hydrostatique (3, 4) comprenant une sortie qui est raccordée à une zone haute pression (14) comprenant un accumulateur haute pression (8), et un ensemble clapet antiretour (17) entre la sortie de la structure hydrostatique (3, 4) et l'accumulateur haute pression (8). Pour améliorer la fonctionnalité d'un mécanisme d'entraînement hydrostatique, l'ensemble clapet antiretour (17) comprend deux clapets de flux principal (18, 19) montés en série conçus sous la forme de clapets de flux principal normalement fermés pour mettre en œuvre un fonctionnement de clapet antiretour dans des directions opposées.
PCT/EP2014/072446 2013-12-04 2014-10-20 Mécanisme d'entraînement hydrostatique et procédé pour faire fonctionner un tel mécanisme WO2015082116A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013224825.3A DE102013224825A1 (de) 2013-12-04 2013-12-04 Hydrostatischer Fahrantrieb
DE102013224825.3 2013-12-04

Publications (1)

Publication Number Publication Date
WO2015082116A1 true WO2015082116A1 (fr) 2015-06-11

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PCT/EP2014/072446 WO2015082116A1 (fr) 2013-12-04 2014-10-20 Mécanisme d'entraînement hydrostatique et procédé pour faire fonctionner un tel mécanisme

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DE (1) DE102013224825A1 (fr)
WO (1) WO2015082116A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018178921A1 (fr) * 2017-03-31 2018-10-04 Ducere Holdings (Pty) Limited Entraînement hydrostatique en boucle ouverte

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005060995A1 (de) * 2005-12-20 2007-06-28 Bosch Rexroth Aktiengesellschaft Hydrostatischer Antrieb mit Rückgewinnung von Bremsenergie
DE102009056153A1 (de) * 2009-11-27 2011-06-01 Robert Bosch Gmbh Antriebssystem mit multifunktionaler Energierückgewinnung und Verfahren zu dessen Betrieb
DE102012208687A1 (de) * 2012-05-24 2013-11-28 Robert Bosch Gmbh Hydrauliksystem für ein Kraftfahrzeug

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005060995A1 (de) * 2005-12-20 2007-06-28 Bosch Rexroth Aktiengesellschaft Hydrostatischer Antrieb mit Rückgewinnung von Bremsenergie
DE102009056153A1 (de) * 2009-11-27 2011-06-01 Robert Bosch Gmbh Antriebssystem mit multifunktionaler Energierückgewinnung und Verfahren zu dessen Betrieb
DE102012208687A1 (de) * 2012-05-24 2013-11-28 Robert Bosch Gmbh Hydrauliksystem für ein Kraftfahrzeug

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