WO2014026798A1 - Tendeur automatique hydraulique - Google Patents

Tendeur automatique hydraulique Download PDF

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Publication number
WO2014026798A1
WO2014026798A1 PCT/EP2013/063983 EP2013063983W WO2014026798A1 WO 2014026798 A1 WO2014026798 A1 WO 2014026798A1 EP 2013063983 W EP2013063983 W EP 2013063983W WO 2014026798 A1 WO2014026798 A1 WO 2014026798A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
valve
tensioner
pressure relief
pressure chamber
Prior art date
Application number
PCT/EP2013/063983
Other languages
German (de)
English (en)
Inventor
Vladimir Baranov
Marco Kowalski
Bernd Hartmann
Original Assignee
Schaeffler Technologies AG & Co. KG
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 Schaeffler Technologies AG & Co. KG filed Critical Schaeffler Technologies AG & Co. KG
Publication of WO2014026798A1 publication Critical patent/WO2014026798A1/fr

Links

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
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H7/10—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley
    • F16H7/12—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley
    • F16H7/1209—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley with vibration damping means
    • F16H7/1236—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley with vibration damping means of the fluid and restriction type, e.g. dashpot
    • 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
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H2007/0802—Actuators for final output members
    • F16H2007/0806—Compression coil springs
    • 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
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H2007/0802—Actuators for final output members
    • F16H2007/0812—Fluid pressure
    • F16H2007/0814—Fluid pressure with valves opening on surplus pressure
    • 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
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H7/0848—Means for varying tension of belts, ropes, or chains with means for impeding reverse motion
    • F16H2007/0859—Check valves
    • 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
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H2007/0889—Path of movement of the finally actuated member
    • F16H2007/0891—Linear path
    • 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
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H2007/0889—Path of movement of the finally actuated member
    • F16H2007/0893—Circular path

Definitions

  • the invention relates to a hydraulic automatic tensioner. This includes:
  • tensioner housing having a housing bottom and a cylinder extending therefrom
  • a piston which can be moved longitudinally in the cylinder and which delimits a hydraulic pressure chamber with the cylinder
  • a non-return valve which runs on the housing bottom and connects the storage space with the pressure chamber, the check valve closing when the pressure in the pressure chamber exceeds the pressure in the storage space,
  • a pressure relief valve which connects the pressure chamber with the reservoir, wherein the pressure relief valve opens when the pressure in the pressure chamber exceeds a predetermined limit pressure.
  • Such automatic tensioners are typically belt tensioners, which pretension the belt of the accessory drive of an internal combustion engine by means of a tensioning roller actuated by the belt tensioner. While the biasing force is generated by the force of a tensioner spring between tensioner housing and piston, the hydraulic part of the tensioner damps the vibrations of the belt drive by means of so-called leakage gap damping.
  • the hydraulic part of the tensioner damps the vibrations of the belt drive by means of so-called leakage gap damping.
  • the present invention seeks to provide a hydraulic automatic tensioner of the type mentioned with an improved characteristic of the pressure relief. Summary of the invention
  • the automatic tensioner comprises a switchable between an open and a closed position control valve, which allows in the open position, the flow through the pressure relief valve and prevents the flow through the pressure relief valve in the closed position.
  • the pressure relief of the tensioner according to the invention can be locked as needed during operation, wherein in the locked state, the force-displacement map would correspond to the map of a comparable tensioner without pressure relief.
  • the adjustability of the pressure relief allows, for example, that the tensioner is operated during the starting process of the internal combustion engine like a tensioner without pressure relief with high reaction forces and accordingly high damping. This is particularly advantageous in internal combustion engine with start-stop function and consequently numerous restarting operations.
  • Another application may be the belt drive of an internal combustion engine with a starter generator, short RSG.
  • the boot process of the Internal combustion engine swapped by means of the RSG train and idler belt of the belt drive, which then located in Switzerlandtrum tensioner should also be operated with high damping, ie without pressure relief.
  • the piston is still longitudinally movable, but fitted with such a small guide clearance in the cylinder that the leakage gap is hydraulically almost and theoretically completely impermeable. This dimensioning of the leakage gap would result in the tensioner being virtually blocked or locked in the retraction direction when the pressure relief is blocked.
  • Such a high rigidity of the tensioner hydraulics may be desirable in the aforementioned starting processes of the internal combustion engine.
  • the characteristic of the open pressure relief is then suitably tuned so that it takes over the function of the leakage gap damping when the tensioner is in the normal operating mode following the starting process of the internal combustion engine.
  • the switch-off pressure relief of the tensioner may also be useful if the belt drive is operated in a speed range of the internal combustion engine with pronounced vibration excitation and in this operating range a strong vibration damping from the tensioner with correspondingly high tension forces should go out.
  • Figure 3 shows the series connection of the control valve and pressure relief valve as a hydraulic circuit symbol
  • FIG. 4 shows an enlarged section of the piston according to FIG. 2 with the control valve closed
  • FIG. 5 shows the enlarged section of the piston according to FIG. 4 with the control valve open
  • FIG. 6 shows the valve seat of the control valve in perspective detail view. Unless otherwise stated, the same or functionally identical features or components are provided with the same reference numbers.
  • FIG. 1 shows a known hydraulic automatic tensioner 1, which pretensions the belt of an auxiliary belt drive of an internal combustion engine.
  • the tensioner comprises the following components: a tensioner housing 2, a piston part 3 movable longitudinally thereto, an elastomer bellows 4 sealing the tensioner hydraulics to the environment, and a helical compression spring acting on the piston part and the tensioner housing in the direction of extension of the tensioner Piston part and the tensioner housing are provided with fastening eyes 6 and 7, at which the tensioner on the Brennkraft- machine on the one hand and on a (not shown) clamping lever with belt tensioner on the other hand is articulated.
  • the tensioner housing 2 is pot-shaped and provided with a cylinder 8 which extends upwards from a housing bottom 9.
  • the piston part 3 comprises a hollow cylindrical piston 10, which is guided longitudinally movably in the cylinder and limits with the cylinder a hydraulic fluid filled pressure chamber 1 1.
  • the latter communicates via a check valve 12 extending at the bottom of the housing with a reservoir 13, which is bounded externally by the tensioner housing and internally by the cylinder in the form of an annular space partially filled with hydraulic fluid.
  • the check valve is designed as a ball valve, wherein the valve ball is closed when the hydraulic fluid pressure in the pressure chamber is greater than in the reservoir.
  • the pressure chamber 1 1 is also connected via a pressure relief valve 15 and the bore 16 in the piston 10 to the reservoir 13.
  • the pressure relief valve is designed as a conical seat valve, wherein the valve cone 17 is clamped between the limit pressure prescribing the valve spring 18 and a valve seat ring 19 in the piston and lifts off the valve seat ring when the pressure in the pressure chamber exceeds the limit pressure.
  • FIGS. 2 to 5 show a piston part 3 according to the invention which, upstream of the pressure relief valve 15, is provided with an operationally switchable control element. Erventil 20 is provided.
  • the control valve is a 2/2-way valve, which is actuated electromagnetically and is normally closed. According to FIG. 4, in this closed position, a pressure-relieving hydraulic fluid flow from the pressure chamber 11 via the pressure relief valve into the reservoir 13 is prevented.
  • the control valve In the energized open valve position according to FIG. 5, the control valve allows the hydraulic fluid flow from the pressure chamber via the pressure relief valve into the reservoir, wherein the pressure relief valve opens when the pressure in the pressure chamber exceeds the predetermined limit pressure.
  • the pressure relief valve is designed here as a plate valve, the valve plate 17 is acted upon by the limit pressure presetting valve spring 18 in the closing direction.
  • the control valve 20 extends including the solenoid of the electromagnet 21 in the longitudinal direction of the piston 10 completely between the pressure chamber 1 1 and the pressure relief valve 15 and closes in the closed position, the electromagnet passing through the inflow bore 22 to the pressure relief valve in the piston. This is done by a solenoid plate acted upon by the electromagnet 23, which is pressed sealingly against the energized in the pressure chamber against a valve seat inserted in the inflow valve seat part 25 (see FIG. 4) when the electromagnet is de-energized.
  • the electromagnet 21 is energized via line 26, so that the armature plate 23 is attracted away from the valve seat part 25 to the electromagnet. In this valve position, the anchor plate releases openings 27 in the valve seat part for flow to the pressure relief valve 15, as shown by the arrows in Figure 5.
  • valve seat member 25 is formed with a substantially T-shaped cross-section as a hollow body which is opposite to the ren renförmigen openings 27 by the anchor plate 23 by means of a cover 28 to the pressure chamber 1 1 out.

Abstract

L'invention concerne un tendeur automatique hydraulique, comprenant un boîtier de tendeur (2) pourvu d'un cylindre (8); un piston (10) guidé longitudinalement dans le cylindre et délimitant avec le cylindre une chambre de pression hydraulique (11); une chambre de stockage hydraulique (13) délimitée par le boîtier du tendeur et le cylindre; une soupape de non-retour (12) reliant la chambre de stockage à la chambre de pression, la soupape de non-retour se fermant lorsque la pression dans la chambre de pression dépasse la pression régnant dans la chambre de stockage; et une soupape de décharge de pression (15) reliant la chambre de pression à la chambre de stockage, la soupape de décharge de pression s'ouvrant lorsque la pression dans la chambre de pression dépasse une pression limite prédéfinie. Selon l'invention, le tendeur automatique comprend une soupape de commande (20) pouvant passer d'une position ouverte à une position fermée. Dans la position ouverte, cette soupape autorise l'écoulement par l'intermédiaire de la soupape de décharge de pression et, dans la position fermée, bloque l'écoulement par l'intermédiaire de cette même soupape de décharge de pression.
PCT/EP2013/063983 2012-08-13 2013-07-03 Tendeur automatique hydraulique WO2014026798A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102012214383 2012-08-13
DE102012214383.1 2012-08-13
DE102012223329.6 2012-12-17
DE201210223329 DE102012223329A1 (de) 2012-08-13 2012-12-17 Hydraulischer Automatikspanner

Publications (1)

Publication Number Publication Date
WO2014026798A1 true WO2014026798A1 (fr) 2014-02-20

Family

ID=49999258

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2013/063983 WO2014026798A1 (fr) 2012-08-13 2013-07-03 Tendeur automatique hydraulique

Country Status (2)

Country Link
DE (1) DE102012223329A1 (fr)
WO (1) WO2014026798A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109882467A (zh) * 2019-04-11 2019-06-14 陈艳艳 一种液压缸安全阀及其应用

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015206356B4 (de) 2015-04-09 2018-08-16 Schaeffler Technologies AG & Co. KG Zugmittelspannanordnung
US10557529B2 (en) 2015-09-15 2020-02-11 Schaeffler Technologies AG & Co. KG Traction mechanism tensioning unit for a traction mechanism
DE102017123480A1 (de) 2017-10-10 2019-04-11 Schaeffler Technologies AG & Co. KG Hydraulische Spannvorrichtung

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20050064970A1 (en) * 2003-09-19 2005-03-24 Katsushi Tanaka Auto tensioner
JP2006266337A (ja) * 2005-03-22 2006-10-05 Showa Corp 油圧式テンショナーの取付構造
JP2007016945A (ja) * 2005-07-08 2007-01-25 Ntn Corp オートテンショナ
DE102007020885A1 (de) * 2007-05-04 2008-11-06 Schaeffler Kg Hydraulischer Riemenspanner mit einem speziellen Kolben
EP2101082A2 (fr) 2008-03-13 2009-09-16 Ntn Corporation Tendeur automatique hydraulique
DE102010034290A1 (de) 2010-08-13 2012-02-16 Schaeffler Technologies Gmbh & Co. Kg Druckbegrenztes hydraulisch gedämpftes Spannsystem

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20050064970A1 (en) * 2003-09-19 2005-03-24 Katsushi Tanaka Auto tensioner
JP2006266337A (ja) * 2005-03-22 2006-10-05 Showa Corp 油圧式テンショナーの取付構造
JP2007016945A (ja) * 2005-07-08 2007-01-25 Ntn Corp オートテンショナ
DE102007020885A1 (de) * 2007-05-04 2008-11-06 Schaeffler Kg Hydraulischer Riemenspanner mit einem speziellen Kolben
EP2101082A2 (fr) 2008-03-13 2009-09-16 Ntn Corporation Tendeur automatique hydraulique
DE102010034290A1 (de) 2010-08-13 2012-02-16 Schaeffler Technologies Gmbh & Co. Kg Druckbegrenztes hydraulisch gedämpftes Spannsystem

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109882467A (zh) * 2019-04-11 2019-06-14 陈艳艳 一种液压缸安全阀及其应用

Also Published As

Publication number Publication date
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