WO2015185252A1 - Groupe hydraulique d'entraînement - Google Patents

Groupe hydraulique d'entraînement Download PDF

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Publication number
WO2015185252A1
WO2015185252A1 PCT/EP2015/058017 EP2015058017W WO2015185252A1 WO 2015185252 A1 WO2015185252 A1 WO 2015185252A1 EP 2015058017 W EP2015058017 W EP 2015058017W WO 2015185252 A1 WO2015185252 A1 WO 2015185252A1
Authority
WO
WIPO (PCT)
Prior art keywords
hydraulic
pressure
valve
hydraulic drive
pressure side
Prior art date
Application number
PCT/EP2015/058017
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 WO2015185252A1 publication Critical patent/WO2015185252A1/fr

Links

Classifications

    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/024—Pressure relief valves
    • 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
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • F15B20/007—Overload
    • 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
    • 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
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K15/00—Check valves
    • F16K15/02—Check valves with guided rigid valve members
    • F16K15/025—Check valves with guided rigid valve members the valve being loaded by a spring
    • 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
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/14—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side with fracturing member
    • F16K17/16—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side with fracturing member with fracturing diaphragm ; Rupture discs
    • 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
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K27/00—Construction of housing; Use of materials therefor
    • F16K27/02—Construction of housing; Use of materials therefor of lift valves
    • F16K27/0209—Check valves or pivoted valves

Definitions

  • the invention relates to a hydraulic drive with at least one
  • Hydraulic machine in a hydraulic system having a low pressure side and a high pressure side.
  • Hybrid drive for a motor vehicle in which a hydraulically operated energy converter and a combustible gas-powered energy converter interact.
  • the object of the invention is the component protection in a
  • Hydraulic drive with at least one hydraulic machine in one
  • Hydraulic system which has a low pressure side and a high pressure side to improve.
  • the task is with a hydraulic drive with at least one
  • Hydraulic machine in a hydraulic system which has a low pressure side and a high pressure side, achieved in that the hydraulic system comprises a pressure relief valve with a Kochberstfunktion to release at an undesirable increase in pressure abruptly a connection between the high pressure side and the low pressure side.
  • the pressure relief valve Depending on the design of the pressure relief valve, it can happen that at relatively low
  • Opening speeds undesirably high pressures in the hydraulic system occur.
  • a high stability of the pressure limiting valve has a rather disadvantageous effect on its opening behavior. Therefore it can be in
  • An error that can lead to a serious error case may be of a mechanical nature, for example mechanical clamping of the components, and / or of an electrical nature, for example a short circuit in electrical components of the hydraulic machine, and / or another type.
  • the hydraulic drive is preferably used to drive a motor vehicle.
  • the motor vehicle may comprise only the hydraulic drive for driving. Then one speaks of a pure hydraulic drive.
  • the motor vehicle may also comprise a further drive, for example an internal combustion engine.
  • a motor vehicle with more than one drive is also referred to as a hybrid drive.
  • Hydraulic hybrid drive called. In the operation of a motor vehicle with the hydraulic drive should under all operating conditions an unintentional
  • High pressure side can be dismantled quickly and easily. As a result, caused by high pressure on the high pressure side movement of the one
  • Hydraulic machines and a high-pressure accumulator is arranged on the low pressure side of the hydraulic system.
  • On the low pressure side of the hydraulic system is for example a
  • Hydraulic medium reservoir or a low-pressure accumulator arranged.
  • Hydraulic medium reservoir or in the low pressure accumulator is
  • Hydraulic medium for example hydraulic oil, arranged, which is acted upon by low pressure.
  • the low pressure is for example
  • the low pressure is significantly lower than a high pressure, which prevails on the high pressure side.
  • a high-pressure accumulator is arranged on the high pressure side.
  • the high-pressure accumulator is used for storing and defined discharge of hydraulic energy.
  • the hydraulic drive comprises, for example, two hydraulic machines, one of which is preferably a hydraulic pump, while the other is preferably a hydraulic motor.
  • the hydraulic machines can preferably be operated both as a hydraulic pump and as a hydraulic motor.
  • the preferably operated as a hydraulic pump hydraulic machine is used, for example, to build up pressure in the high-pressure accumulator.
  • About the preferably operated as a hydraulic motor hydraulic machine stored in the high-pressure accumulator hydraulic energy can be used to drive at least one driven wheel of the vehicle.
  • Another preferred embodiment of the hydraulic drive is characterized in that the Kochberstfunktion in a valve piece of the
  • Pressure relief valve is integrated.
  • the valve piece is used, for example, to represent a valve seat of the pressure relief valve.
  • the Kochberstfunktion serves as a rupture disc, the one
  • High pressure side closes. As soon as a pressure on the high-pressure side exceeds a predetermined pressure value, the rupture disk ruptures, so that a rapid pressure reduction takes place from the high-pressure side to the low-pressure side.
  • a further preferred embodiment of the hydraulic drive is characterized in that the Mattertownstfunktion is integrated in a valve piston of the pressure relief valve.
  • the overpressure bursting function is special advantageously integrated in a closing body, which is formed on the valve piston.
  • the closing body closes a high-pressure channel, which is opened when the closing body lifts off from a valve seat of the pressure-limiting valve.
  • a further preferred embodiment of the hydraulic drive is characterized in that the pressure relief valve comprises a rupture disk.
  • the pressure-dependent rupture of the rupture disk leads to an abrupt pressure reduction in the case of impermissibly high pressure overshoots in the hydraulic system.
  • the rupture disk can be designed, for example, as a thin steel disk.
  • a further preferred embodiment of the hydraulic drive is characterized in that the rupture disk is arranged in a connecting channel, the high-pressure side in the pressure relief valve with the
  • the rupture disk can, for example, in the
  • High pressure side should be done so that damage to components of the hydraulic system is omitted.
  • Another preferred embodiment of the hydraulic drive is characterized in that the rupture disk is fixed between two sleeves, which are arranged in the connecting channel. With the two sleeves, the rupture disc can be fixed in a simple manner in the connecting channel.
  • Bursting disc module are combined.
  • the rupture disk module can be replaced quickly and easily if the overpressure burst function has been triggered in the pressure relief valve.
  • the invention further relates to a pressure relief valve with a Kochberstfunktion for a hydraulic drive described above.
  • the Kochberstfunktion allows in a simple manner in the previously described serious error cases avoiding too high pressure overshoot. This can be safely prevented in a simple manner that external leakage occurs.
  • the components of the hydraulic system are safely protected from an undesirably high pressure.
  • the invention further relates to a rupture disk, in particular a
  • Bursting disc module for a previously described pressure relief valve.
  • the rupture disk in particular the rupture disk module, can be traded separately.
  • Figure 1 is a simplified representation of a hydraulic drive of a motor vehicle with a pressure relief valve according to the invention, which has a Mathtigberstfunktion;
  • FIG. 2 shows the pressure limiting valve from FIG. 1 with a rupture disk module in longitudinal section
  • Figure 3 is an enlarged view of the rupture disk module of Figure 2 in longitudinal section and
  • FIG. 4 shows a valve piston of the pressure limiting valve from FIG. 2 with a bursting disk module, as shown in FIG. 3, in longitudinal section.
  • FIG. 1 shows in simplified form a hydraulic drive 10 of a motor vehicle.
  • the hydraulic drive 10 is drivingly connected to a driven wheel (not shown) in, for example, the drive train of a motor vehicle.
  • the driven wheel can be connected, for example via a differential drivingly to the hydraulic drive 10, which can also be referred to as a hydrostatic drive.
  • Embodiment to a pure hydraulic drive Other than shown, the hydraulic drive 10 but also part of a
  • Hydraulic hybrid powertrain of a motor vehicle Hydraulic hybrid powertrain of a motor vehicle.
  • a hydraulic hybrid drive train also includes another drive as a primary or secondary drive.
  • the further drive is, for example, an internal combustion engine, which is also known as
  • the hydraulic drive 10 comprises a first hydraulic machine 11 and a second hydraulic machine 12.
  • the two hydraulic machines 11 and 12 are hydraulically connected to a low-pressure side 13 on the input side.
  • the low pressure side 13 includes a low pressure accumulator 14 with
  • Hydraulic medium which is subjected to low pressure.
  • the low pressure accumulator 14 may also be referred to as a hydraulic medium reservoir.
  • the high-pressure side 16 comprises a high-pressure accumulator 17 with hydraulic medium, which is subjected to high pressure.
  • Hydraulic machines 11 and 12 which are indicated only by rectangles, are for example axial piston machines.
  • the hydraulic machines 11 and 12 can advantageously be operated both as a hydraulic motor and as a hydraulic pump. In one
  • Hydraulic hybrid powertrain the hydraulic machine 11 is preferred as Hydraulic pump operated.
  • the hydraulic machine 12 is in the
  • Hydraulikhybridantriebsstrang preferably operated as a hydraulic motor.
  • Valve device 21 is preferably a storage valve or a
  • Accumulator charging valve which is connected on the high pressure side 16 between the outputs of the hydraulic machines 11 and 12 and the high pressure accumulator 17.
  • an optional filter device is indicated.
  • the hydraulic machines 11, 12 is preferably a so-called
  • the low pressure side 13 and the high pressure side 16 of the hydraulic drive 10 represent a hydraulic system 25, which in addition to the two hydraulic machines 11, 12, the
  • Low-pressure accumulator 14 the high pressure accumulator 17 and the valve device 21 comprises a high pressure line 26, a low pressure line 28 and a leakage line 27.
  • the high pressure line 26 is associated with the high pressure side 16 and with
  • the low pressure line 28 is associated with the low pressure side 13 and acted upon by low pressure.
  • the leakage line 27 is with
  • Main flow valve of the hydraulic machine 11 is no longer working properly. It may happen, for example, that the main flow valve of the hydraulic machine 11 no longer receives power through a connector waste and remains permanently open. However, the main flow valve of the hydraulic machine 11 can also remain incorrectly open by jamming a closing body. About the open main flow valve of the hydraulic machine 11 may cause an undesirable increase in pressure on the high pressure side 16.
  • Pressure relief valve 30 arranged with a Kochberstfunktion.
  • the overpressure bursting function ensures that in the event of serious errors, one too high pressure or too high pressure overshoot in the
  • Hydraulic system 25 is avoided by connecting the high pressure side 16 to the low pressure side 13 or be.
  • FIG. 2 shows an embodiment of the pressure relief valve 30 with the Mattertownberstfunktion of Figure 1 is shown in longitudinal section.
  • Pressure relief valve 30 with the overpressure bursting function is in one
  • the housing body 35 installed.
  • the housing body 35 is a component of the hydraulic system 25.
  • the housing body 35 may also be a housing component of a hydraulic machine.
  • the housing body 35 includes for receiving the pressure relief valve 30 has a receiving bore 40. From the receiving bore 40 go
  • a valve piece 45 is in the receiving bore 40 in the region of the high pressure passage 41 and the
  • Low pressure channel 42 is arranged.
  • a sealing ring 46 is arranged in the region of the high-pressure passage 41 between the valve piece 45 and the housing body 35.
  • the valve piece 45 is by means of a locking screw 48 in the
  • the locking screw 48 comprises with the valve piece 45 a central cavity in which a valve piston 50 and a compression spring 52 are received.
  • valve piston 50 is guided in the valve piece 45, in Figure 2 upwards and downwards, movable back and forth.
  • the compression spring 52 is supported with its upper end in Figure 2 on a shim 53.
  • the shim 53 is between the upper end of the compression spring 52 in Figure 2 and the
  • the lower end of the compression spring 52 in FIG. 2 is biased against the valve piston 50.
  • the valve piston 50 has at its the compression spring 52nd
  • the closing body 54 serves to represent a valve seat of the pressure-limiting valve 30 and, in its closed position shown in FIG. 2, closes a connecting channel 60.
  • connection channel 60 creates a connection between a valve space 56 in the valve piece 45 and the high-pressure channel 41 in the housing body 35. From the valve space 56 there are further two connection channels 58, 59 connecting the valve space 56 to the low-pressure channel 42 in the housing body 35 ,
  • the pressure compensation channel 61 extends through the valve piston 50 and creates a pressure equalization connection between the valve chamber 56 and a receiving space for the compression spring 52.
  • the pressure compensation channel 62 extends from the connecting channel 59 through the valve piece 45 into the receiving space for the compression spring 52nd In FIG. 2, the valve piece 45 moreover comprises a further one
  • Connecting channel 65 The connecting channel 65 provides an additional connection between the connecting channel 60 in the valve piece 45 and the low-pressure channel 42 in the housing body 35th
  • a bursting disk module 66 is arranged in the connecting channel 65.
  • the bursting disk module 66 opens at extreme pressure overshoots
  • FIG. 3 shows that the bursting disk module 66 from FIG. 2 comprises a rupture disk 70.
  • the rupture disk 70 is clamped between two sleeves 71, 72.
  • the sleeves 71, 72 are, for example, pressed into the connecting channel (65 in FIG. 2).
  • the rupture disk 70 is materially connected to the two sleeves 71, 72.
  • the cohesive connection can be produced, for example, by welding.
  • Connecting channel 75 of the valve piston 50 can be arranged.
  • the connecting channel 75 extends through the closing body 54 of the
  • Valve piston 50 The bursting disc module 66 is for example in the

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Safety Valves (AREA)

Abstract

Groupe hydraulique d'entraînement (10) qui comporte au moins un moteur hydraulique (11, 12) situé dans un système hydraulique (25) présentant un côté basse pression (13) et un côté haute pression (16). L'objet de la présente invention est d'améliorer la protection des composants d'un groupe hydraulique d'entraînement. À cet effet, ledit système hydraulique (25) comporte une soupape de limitation de pression (30) pourvue d'une fonction d'éclatement en cas de surpression, qui, en cas d'élévation indésirable de la pression, permet de libérer brutalement une liaison entre le côté haute pression (16) et le côté basse pression (13).
PCT/EP2015/058017 2014-06-03 2015-04-14 Groupe hydraulique d'entraînement WO2015185252A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014210400.9 2014-06-03
DE102014210400.9A DE102014210400A1 (de) 2014-06-03 2014-06-03 Hydraulikantrieb

Publications (1)

Publication Number Publication Date
WO2015185252A1 true WO2015185252A1 (fr) 2015-12-10

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2015/058017 WO2015185252A1 (fr) 2014-06-03 2015-04-14 Groupe hydraulique d'entraînement

Country Status (2)

Country Link
DE (1) DE102014210400A1 (fr)
WO (1) WO2015185252A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018214097A1 (de) * 2018-08-21 2020-02-27 Zf Friedrichshafen Ag Verfahren zum Steuern eines stufenlosen Getriebes

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3722068C1 (en) * 1987-07-03 1988-09-29 Bosch Gmbh Robert Burst-proof valve
US6148841A (en) * 1999-07-08 2000-11-21 Davidson; Gilbert High pressure gas valve
EP2019240A1 (fr) * 2007-07-26 2009-01-28 MOOG GmbH Soupape de commande de charge hydraulique à circuit RC
DE102011002967A1 (de) * 2011-01-21 2012-07-26 Robert Bosch Gmbh Hybridantrieb für ein Kraftfahrzeug

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3722068C1 (en) * 1987-07-03 1988-09-29 Bosch Gmbh Robert Burst-proof valve
US6148841A (en) * 1999-07-08 2000-11-21 Davidson; Gilbert High pressure gas valve
EP2019240A1 (fr) * 2007-07-26 2009-01-28 MOOG GmbH Soupape de commande de charge hydraulique à circuit RC
DE102011002967A1 (de) * 2011-01-21 2012-07-26 Robert Bosch Gmbh Hybridantrieb für ein Kraftfahrzeug

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018214097A1 (de) * 2018-08-21 2020-02-27 Zf Friedrichshafen Ag Verfahren zum Steuern eines stufenlosen Getriebes

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Publication number Publication date
DE102014210400A1 (de) 2015-12-03

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