WO2013079320A1 - Composant hydrodynamique - Google Patents

Composant hydrodynamique Download PDF

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Publication number
WO2013079320A1
WO2013079320A1 PCT/EP2012/072543 EP2012072543W WO2013079320A1 WO 2013079320 A1 WO2013079320 A1 WO 2013079320A1 EP 2012072543 W EP2012072543 W EP 2012072543W WO 2013079320 A1 WO2013079320 A1 WO 2013079320A1
Authority
WO
WIPO (PCT)
Prior art keywords
component
actuating element
hydrodynamic
hydrodynamic component
movement
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.)
Ceased
Application number
PCT/EP2012/072543
Other languages
German (de)
English (en)
Inventor
Werner Adams
Achim Menne
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.)
Voith Patent GmbH
Original Assignee
Voith Patent 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 Voith Patent GmbH filed Critical Voith Patent GmbH
Publication of WO2013079320A1 publication Critical patent/WO2013079320A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D47/00—Systems of clutches, or clutches and couplings, comprising devices of types grouped under at least two of the following sets of groups: F16D1/00 - F16D9/00, F16D11/00 - F16D23/00, F16D25/00 - F16D29/00, F16D31/00 - F16D39/00, F16D41/00 - F16D45/00
    • F16D47/06—Systems of clutches, or clutches and couplings, comprising devices of types grouped under at least two of the following sets of groups: F16D1/00 - F16D9/00, F16D11/00 - F16D23/00, F16D25/00 - F16D29/00, F16D31/00 - F16D39/00, F16D41/00 - F16D45/00 of which at least one is a clutch with a fluid or a semifluid as power-transmitting means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T10/00—Control or regulation for continuous braking making use of fluid or powdered medium, e.g. for use when descending a long slope
    • B60T10/02—Control or regulation for continuous braking making use of fluid or powdered medium, e.g. for use when descending a long slope with hydrodynamic brake
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
    • F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
    • F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
    • F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D48/00—External control of clutches
    • F16D48/02—Control by fluid pressure
    • F16D2048/0212—Details of pistons for primary or secondary cylinders especially adapted for fluid control

Definitions

  • the invention relates to a hydrodynamic component according to the closer defined in the preamble of claim 1. Art also relates to a
  • the object of the present invention is now a
  • hydrodynamic component having the features in the characterizing part of claim 1.
  • the hereof dependent subclaims indicate advantageous developments and refinements of the hydrodynamic component according to the invention.
  • an actuator for moving an actuating element of the mechanical coupling from a first to a second position is available.
  • the movable over the actuating element coupling elements are in the second position of
  • the embodiment according to the invention now provides that a device is also provided for the sudden movement of the actuating element into the second position.
  • a sudden movement is achieved that when filled or simultaneously to actuate the mechanical clutch starting filling the working space with a working fluid, the second position is reached before in the working space a stronger meridional flow in the working fluid between the at least one rotatable component and the second component forms.
  • the device for sudden movement of the actuating element via a pulse thus ensures that the mechanical clutch is already completely closed and slip-free engagement before, even with already filled with working fluid hydrodynamic component, the significant meridional flows and thus forms the hydrodynamic component with the significant transmission of torque begins.
  • a synchronization between the driven shaft and the rotatable component of the hydrodynamic component is achieved before in the
  • hydrodynamic component builds up the torque. This reduces the synchronization work to an absolute minimum. This reduces the thermal load of the mechanical clutch or a
  • the device for the sudden movement of the hydrodynamic component it is provided that the device for the sudden movement of the hydrodynamic component
  • Actuator having a pneumatically actuable piston, which includes a cylinder with a first space for the actuating medium and a second space for the actuating medium, wherein with onset of movement, a connection of the first space with the second space is formed.
  • a pneumatically actuated piston utilizes the first air entering the first space as a kind of gas spring. The air condenses without reaching a breakaway force of the piston. As a result, the piston is under
  • Preload set Starts the movement, then a connection between the first and the second space is free, so that the second space is filled not only by the inflowing actuating medium, but also from the already under bias or an increased pressure medium of the first space.
  • a sudden closing of the clutch by moving the
  • Coupling elements in a position in which they are in slip-free engagement with each other, achieved.
  • prestressed air before the biased air movement after the completed movement is greater than the ratio of the effective area before movement to the effective area after the completed movement.
  • the ratio of the prestressed air before the movement to the prestressed air after the closed movement is at least a factor of 1.8 greater than the ratio of the effective area before movement to the effective area after the completed movement.
  • the device for abrupt movement of the actuating element has at least two mutually acting spring elements between the actuating element and the actuator, of which at least one is designed as a tilt spring. If at least one - but not all - of the spring elements as tipping spring
  • Tilt spring element formed spring element by the operation of the
  • This bias acts first on the at least one
  • Tilting spring as the typically weaker spring element, so that it does not come to a movement of the actuating element, but to a "charging" or biasing the tipping spring
  • Such a tipping spring is designed so that it abruptly overturns from a certain force and, for example In this way, a sudden movement of the actuating element is made possible by an impulse.
  • the means for abrupt movement of the actuating element comprises at least one spring element which is biased against a holding element of the actuator, wherein a triggering of the holding element releases the bias abruptly.
  • the means for abrupt movement of the actuating element comprises at least one spring element which is biased against a holding element of the actuator, wherein a triggering of the holding element releases the bias abruptly.
  • spring element which is formed for example as a plate spring, coil spring or as a gas pressure spring.
  • the actuator presses on this Spring element and sets this under bias, wherein the actuating element and / or the spring element actively by a retaining element against this
  • Preload is maintained. From a certain bias can then take place active or automatic triggering of the holding element.
  • This can for example be designed as a permanent magnet or as an electromagnet.
  • a mechanical retaining pawl which in the manner of a mechanical release of the actuating element or the spring element under bias voltage holding position in a
  • Actuating element or the spring element releasing position can be moved. All these variants make it possible to build a bias of the spring element, which then activates abruptly activated from a certain force or by a trigger signal to the actuator and thus ensures a very fast pulse-like movement of the coupling elements in their slip-free engagement each other located position.
  • the hydrodynamic component according to the invention can in particular be a switchable or disconnectable retarder or a
  • hydrodynamic components which constantly in the region of their working space at least a certain amount of
  • Components in which the torque transmission starts very quickly can be through the inventive design with a device for abrupt movement of the actuator to reduce the synchronization work to a minimum.
  • the result is a very low-wear construction.
  • Embodiment of the hydrodynamic component according to the invention be constructed as a pure friction elements which synchronize via the friction and then ensure a slip-free connection in the second position of the actuating element on the surface friction between the coupling elements.
  • the coupling elements in the manner of a synchronized dog clutch, in particular with claws oriented obliquely to the axial direction, so that after the synchronization a slip-free positive connection is given and due to the inclined claws releasing the clutch without additional actuator,
  • Figure 1 is a schematic representation of a hydrodynamic component in a drive train
  • Figure 2 shows a first possible embodiment of a device for
  • Figure 3 shows a second possible embodiment of a device for the sudden movement of an actuating element of a mechanical coupling
  • Figure 4 shows a third possible embodiment of a device for
  • Figure 5 shows a fourth possible embodiment of a device for
  • Figure 6 shows a fifth possible embodiment of a device for
  • a principle drive train 1 can be seen, as it may be used for example in a commercial vehicle.
  • Drive train 1 comprises a drive motor 2, for example a diesel engine. This is connected via a shaft 3 with a gear 4. This can be designed for example as an automatic transmission. Part of the transmission 4 may also be further drive means such as an electric motor for hybridization of the drive train 1. From the gear 4 leads a
  • Output shaft 5 for example, to a differential through which the wheels of the utility vehicle, the rail vehicle or the like are driven.
  • the transmission 4 also has a manner known per se
  • a hydrodynamic component 7 may be arranged, which in the illustrated here
  • Embodiment a retarder 8 and a mechanical coupling. 9 includes.
  • the retarder 8 as hydrodynamic brake is located in the embodiment shown here, a stator 10 and a rotatable component in the form of a rotor 11, which together form a toric working space
  • Working fluid such as oil or water, constructed in the toroidal working space between the stator 10 and the rotor 11 with a driven rotor 11, a flow which transmits a torque from the rotor 11 to the stator 10 and thereby the rotor 11 and the via the clutch 9 with it brakes connected shaft 6.
  • a gear stage could be provided between the rotor 11 and the clutch 9.
  • hydrodynamic component of course also be a hydrodynamic coupling, a so-called turbo coupling, a hydrodynamic converter or a hydrodynamic Trilok converter.
  • the aim is to be able to take this as quickly as possible in the detachable retarder 8 in the hydrodynamic component 7 in order, in the case of
  • mechanical coupling 9 in this case connects the driven shaft 6 with the rotor 11 and thus ensures that in the retarder 8 the desired
  • Working medium is filled or already filled with the working fluid.
  • the rotor 11 as a rotatable component of the hydrodynamic component 7 from a stationary state in a rotating at the same speed as the shaft 6 state be accelerated.
  • a comparatively high synchronization work typically has to be performed in order to obtain the required torque from the first contact, for example, of friction coupling elements to the slip-free transmission of the torque
  • the mechanical coupling 9 of the hydrodynamic component 7 shown here has a
  • the mechanical clutch 9 is constructed as a friction clutch.
  • the construction as a synchronized dog clutch would also be conceivable.
  • a claw coupling with inclined claws, as at an angle to the radial direction running claws is particularly useful.
  • the following examples will be described with reference to a friction clutch. However, they can be easily transferred by the skilled person to a synchronized jaw clutch.
  • an actuator 18 is present, which is formed in the embodiment shown here as a pneumatic actuator. If necessary, compressed air is pressed into the region of a cylinder 20 between the cylinder 20 and a piston 21 via an indicated line 19. If the piston 21 is located on the left side of the cylinder 20 shown in the drawing, then first a space designated by I between the piston 21 and the cylinder 20 will be filled with the compressed air. As long as a breakaway force of the cylinder 21 is not exceeded, the compressed air will accumulate in the first space I and reach a certain pressure or a bias in the manner of a gas spring. Only after the breakaway force has been exceeded, a second, designated in the illustration with II space is released. In addition to the influx of compressed air via the line 19 into the second space II, the already biased compressed air from the first room I will also at least partially flow into this room II. This results in a sudden pulse-like movement of the piston 21 and consequently the actuating element 14.
  • prestressed air before the movement to the prestressed air after the completed movement to be greater, preferably more than 1.8 times, than the ratio of the effective area (piston area of the space I) before Movement to the effective area (total effective area of the piston 21) after the completed movement.
  • a second embodiment of the mechanical coupling 9 is in the
  • This can be formed for example as a permanent magnet or as an electromagnet.
  • compressed air or other gaseous actuating medium is introduced via the line 19.
  • the magnetically formed piston 21 is held against the build-up pressure force of the compressed air with a certain force. Only above a certain force, the bias between cylinder 20 and piston 21 exceeds the sum of the opposing forces, so that the piston 21 is moved abruptly and the actuator 14 moves very quickly in a second clutch 9 closing position. This also makes it possible to realize a very fast movement of the clutch 9 with the advantages already mentioned above.
  • Adhesive element 22 on the piston 21 in this case formed so that they are sealingly against each other, so that here no compressed air between the two elements penetrate and can affect the magnetic adhesion. Furthermore, the effect can - be amplified - analogous to the embodiments of Figure 2. Namely, the sealed portion is released only after release from the magnetic adhesive member 22 for the pre-compressed air. Through this release, the actuation force then increases abruptly.
  • a third embodiment can be seen in the illustration of FIG. Again, a magnetic adhesive element 22 is again present, which this time is designed differently and the actuator 14 holds directly.
  • the actuator 18 again comprises a piston 21 in the cylinder 20. It can be moved pneumatically or in this case also hydraulically or possibly also by an electric motor. Between the piston 21 and the
  • Actuator 14 is arranged in the embodiment shown here, a spring element 23 in the form of a plate spring.
  • the functionality is essentially the same as in the structure shown in FIG.
  • the plate spring 23 which is designed so that it is biased by the piston 21 accordingly.
  • the actuating element 14 is abruptly moved against the friction linings 13 and the counter-element 16. Again, the effect is a very fast closing mechanical coupling 9, which ensures synchronization in such a short time that the friction losses are minimal, since typically the meridional flow in the retarder 8 is not yet established when the elements of the clutch 9 already in slip-free engagement with each other.
  • FIG. 1 A further alternative embodiment can be seen in the representation of FIG.
  • the structure again shows the actuator 18 in a manner analogous to the representation in FIG. 4.
  • a plate spring 23 is also provided here.
  • a tilt spring 24 is also provided, which is connected in its action against the plate spring 23.
  • the characteristic of such a tilt spring 24 is now that by a bias voltage due to the spring 23, the tilt spring remains in a first position until the force of the plate spring 23 exceeds a certain amount. Then there is a sudden tipping over of the tilt spring 24, for example, from a concave to a convex shape. As a result, the actuating element 14 is also abruptly moved and the mechanical coupling 9 closes.
  • a fifth embodiment can be seen in the representation of FIG. It essentially corresponds to the embodiment which has already been illustrated in FIG. However, the magnetic adhesive element 22 is dispensed with.
  • an intermediate element 25 is arranged between the plate spring 23 and the actuating element 14.
  • This intermediate element 25, which is not structurally necessary, but also by the Actuator 14 may be formed integrally with, is used in the embodiment shown here to be held by a mechanical holding pawl 26, while by a movement of the piston 21, a bias on the plate spring 23 is constructed.
  • the mechanical retaining pawl 26 after a sufficient bias has been applied to the plate spring 23, for example, active, be withdrawn. Then again there is a sudden movement, in this case the intermediate element 25 against the

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Transportation (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)

Abstract

L'invention concerne un composant hydrodynamique, comprenant un espace de travail de forme torique formé par au moins deux éléments dont un au moins est réalisé sous la forme d'un élément mobile en rotation dans l'espace de travail ; un accouplement mécanique pour relier le ou les éléments mobiles à un arbre mené ; un actionneur servant à déplacer un organe d'actionnement de l'accouplement mécanique d'une première dans une deuxième position ; des organes d'accouplement qui peuvent être déplacés au moyen de l'organe d'actionnement de façon à amener les organes d'accouplement en prise l'un avec l'autre sans glissement dans la deuxième position de l'organe d'actionnement. L'invention est caractérisée en ce qu'il est prévu un système permettant de déplacer brusquement l'organe d'actionnement dans la deuxième position de telle façon que, lorsque l'espace de travail est rempli d'un fluide de travail ou lorsque son remplissage commence en même temps que l'actionnement de l'accouplement mécanique, la deuxième position est atteinte avant qu'un écoulement méridien se forme dans l'espace de travail entre le ou les éléments mobiles en rotation et le ou les deuxièmes éléments.
PCT/EP2012/072543 2011-12-02 2012-11-14 Composant hydrodynamique Ceased WO2013079320A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011119990.3 2011-12-02
DE102011119990.3A DE102011119990B4 (de) 2011-12-02 2011-12-02 Hydrodynamische Komponente

Publications (1)

Publication Number Publication Date
WO2013079320A1 true WO2013079320A1 (fr) 2013-06-06

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PCT/EP2012/072543 Ceased WO2013079320A1 (fr) 2011-12-02 2012-11-14 Composant hydrodynamique

Country Status (2)

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DE (1) DE102011119990B4 (fr)
WO (1) WO2013079320A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015072912A1 (fr) * 2013-11-18 2015-05-21 Scania Cv Ab Dispositif d'embrayage destiné à un ralentisseur
WO2015126313A1 (fr) * 2014-02-19 2015-08-27 Scania Cv Ab Unité de commande pour ralentisseur, véhicule comprenant ledit ralentisseur et procédé pour assurer la mise en prise d'un ralentisseur

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013224095A1 (de) 2013-11-26 2015-05-28 Voith Patent Gmbh Hydrodynamische Maschine
WO2015192861A1 (fr) * 2014-06-17 2015-12-23 Volvo Truck Corporation Commande d'embrayage améliorée

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1293451A (fr) * 1961-06-28 1962-05-11 Automotive Prod Co Ltd Dispositif de transmission à fluide, notamment pour véhicules automobiles
DE1700160B1 (de) * 1962-08-16 1971-03-11 Twin Disc Inc Getriebe mit einer einem hydrodynamischen drehmomentwandler vorgeschalteten rutschkupplung
US5285872A (en) * 1991-03-25 1994-02-15 Akebono Brake Industry Co., Ltd. Hydraulic retarder having a fluid filled casing with a rotor operating clutch disposed therein
EP1251050A2 (fr) * 2001-04-18 2002-10-23 ZF FRIEDRICHSHAFEN Aktiengesellschaft Systéme de freinage et ralentisseur
US20070125614A1 (en) * 2004-09-15 2007-06-07 Yoshiharu Sato Control device for input clutch of work vehicle
DE102009001146A1 (de) * 2009-02-25 2010-08-26 Zf Friedrichshafen Ag Antriebsstrang eines Kraftfahrzeugs und Verfahren zu dessen Steuerung
EP2024209B1 (fr) 2007-05-25 2011-04-27 Voith Patent GmbH Procédé pour commander un frein hydrodynamique

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DE4444242B4 (de) * 1993-12-23 2004-07-08 Volkswagen Ag Kupplungsanordnung für ein Kraftfahrzeug
DE19527292C2 (de) * 1995-07-26 1999-05-12 Tueschen & Zimmermann Durchschalteinrichtung für eine hydrodynamische Strömungskupplung
DE19804635C2 (de) * 1998-02-06 2001-03-01 Mannesmann Sachs Ag Hydrodynamische Kupplungseinrichtung mit einer Überbrückungskupplung
BR0010766A (pt) * 1999-03-12 2002-01-15 Voith Turbo Kg Unidade de partida
JP2004507690A (ja) * 2000-08-31 2004-03-11 ヴォイス・ターボ・ゲーエムベーハー・ウント・コ・カーゲー 始動ユニット、及び始動ユニットを異なる限界条件を有する駆動システムに、特に異なる駆動機械に適合させるための方法
DE102007002172A1 (de) * 2007-01-15 2008-07-24 Zf Friedrichshafen Ag Vorrichtung zum Übertragen eines Drehmomentes und Verfahren zum Betreiben einer solchen Vorrichtung
DE102009039077A1 (de) * 2008-09-18 2010-04-01 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Kraftübertragungsvorrichtung

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1293451A (fr) * 1961-06-28 1962-05-11 Automotive Prod Co Ltd Dispositif de transmission à fluide, notamment pour véhicules automobiles
DE1700160B1 (de) * 1962-08-16 1971-03-11 Twin Disc Inc Getriebe mit einer einem hydrodynamischen drehmomentwandler vorgeschalteten rutschkupplung
US5285872A (en) * 1991-03-25 1994-02-15 Akebono Brake Industry Co., Ltd. Hydraulic retarder having a fluid filled casing with a rotor operating clutch disposed therein
EP1251050A2 (fr) * 2001-04-18 2002-10-23 ZF FRIEDRICHSHAFEN Aktiengesellschaft Systéme de freinage et ralentisseur
US20070125614A1 (en) * 2004-09-15 2007-06-07 Yoshiharu Sato Control device for input clutch of work vehicle
EP2024209B1 (fr) 2007-05-25 2011-04-27 Voith Patent GmbH Procédé pour commander un frein hydrodynamique
DE102009001146A1 (de) * 2009-02-25 2010-08-26 Zf Friedrichshafen Ag Antriebsstrang eines Kraftfahrzeugs und Verfahren zu dessen Steuerung

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015072912A1 (fr) * 2013-11-18 2015-05-21 Scania Cv Ab Dispositif d'embrayage destiné à un ralentisseur
WO2015126313A1 (fr) * 2014-02-19 2015-08-27 Scania Cv Ab Unité de commande pour ralentisseur, véhicule comprenant ledit ralentisseur et procédé pour assurer la mise en prise d'un ralentisseur

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Publication number Publication date
DE102011119990B4 (de) 2015-10-29
DE102011119990A1 (de) 2013-06-06

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