WO1984003337A1 - Dispositif de commande pour embrayage - Google Patents

Dispositif de commande pour embrayage Download PDF

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Publication number
WO1984003337A1
WO1984003337A1 PCT/EP1984/000003 EP8400003W WO8403337A1 WO 1984003337 A1 WO1984003337 A1 WO 1984003337A1 EP 8400003 W EP8400003 W EP 8400003W WO 8403337 A1 WO8403337 A1 WO 8403337A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
valve
filling
clutch
line
Prior art date
Application number
PCT/EP1984/000003
Other languages
German (de)
English (en)
Inventor
Alfred Magg
Franz Boss
Gerold Bieber
Original Assignee
Zahnradfabrik Friedrichshafen
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 Zahnradfabrik Friedrichshafen filed Critical Zahnradfabrik Friedrichshafen
Priority to BR8406983A priority Critical patent/BR8406983A/pt
Publication of WO1984003337A1 publication Critical patent/WO1984003337A1/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
    • 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
    • F16D25/0638—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 with more than two discs, e.g. multiple lamellae
    • 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
    • F16D25/12—Details not specific to one of the before-mentioned types
    • F16D25/14—Fluid pressure control
    • 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
    • F16D43/00—Automatic clutches
    • F16D43/28—Automatic clutches actuated by fluid pressure
    • F16D43/284—Automatic clutches actuated by fluid pressure controlled by angular speed
    • 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
    • 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
    • F16D48/04—Control by fluid pressure providing power assistance
    • 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
    • F16D2048/0209—Control by fluid pressure characterised by fluid valves having control pistons, e.g. spools
    • 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
    • F16D2048/0221—Valves for clutch control systems; Details thereof

Definitions

  • This invention relates to a control device for a clutch according to the preamble of claim 1.
  • Such a control device is e.g. B. from DE-OS 29 41 935 known.
  • a soft, driving-state-dependent push / pull circuit is possible according to this document, the construction effort to arrive at such a result still seems too high and the sequence of the circuit still takes too much time.
  • the mass of the piston and the spring is easily compensated by the filling and cutting emptying valve, so that even at a comparatively high speed with a relative low switching pressure - system pressure - the supply to the outer pressure chamber is guaranteed.
  • the pressure chamber filled first transmits part of the engine torque and the control valve switches on the second pressure chamber - i.e. the radially inner pressure chamber - solely as a function of the pressure in the radially outer pressure chamber, in addition to a coupling that is well adapted to the driving condition, a fast transmission of the maximum possible torque achieved with great simplification.
  • the arrangement of the pulse valve in connection with the large-volume lines for the simultaneous supply of the pressure medium for actuating the clutch and the coolant and lubricant for cooling the lamellae is particularly advantageous, this pulse valve solely from the collapse of the pressure in the supply line to the holding valve is switched to flow if this has been switched to flow by the solenoid valve.
  • the pulse valve closes automatically and the accumulators can refill. Lubricant is supplied to the clutch only in the slipping phase, but then very strongly. If no control valve for filling the internal pressure space, but, according to claim 10, only a pressure relief valve or only a throttle is arranged, a further simplification is possible. Further details of the invention will be explained with reference to an exemplary embodiment and with reference to drawings, the details of the drawing being the subject of the invention.
  • Fig. 1 shows the part of a control device for a converter clutch, in particular the area of the clutch.
  • Fig. 2 shows a half section through the clutch in
  • Fig. 3 shows a half section through the clutch in
  • FIG. 4 is a diagram of the transmission torques of the clutch as a function of the radially outer pressure chamber and the speed of the clutch carrier.
  • Fig. 5 is a diagram of the transmission torques of the clutch as a function of the radially inner pressure space and the speed of the clutch carrier.
  • 1 shows the part of a control system for a converter clutch that is relevant for a clutch.
  • 1 is the clutch itself with the radially outer pressure chamber 4 and the radially inner pressure chamber 6, both of which act to close the clutch on the pressure piston 12 and this on the disk pack 11, the pressure piston being pushed back into the open position by a spring 13 .
  • 3 designates a filling and line emptying valve and 5 a control valve, both of which are arranged in or on the coupling carrier 14 (FIGS. 2 and 3).
  • the switching valve 9, pulse valve 8 and solenoid valve 95 are fixed and mounted in or on the housing 15 (FIG. 3) of the clutch.
  • the coolant 71 and pressure medium accumulator 75 are also primarily arranged on the housing 15 of the clutch 1.
  • the filling and Schneilentlee ⁇ tion valve 3 is connected via a filling and emptying channel 41 to the radially outer pressure chamber 4 and via an emptying channel 61 to the radially inner pressure chamber 6. Both channels have large cross sections for a relatively quick filling or emptying.
  • a feed line 56 and a control line 55 branch off from the filling and emptying channel 41 for the control valve 5.
  • the connecting line 38 from the switching valve 9 to the filling and draining valve 3 is expanded in the area of the coupling carrier 14 to a chamber 2, from which a control line 37 branches off.
  • the switching valve 9 is connected to the pulse valve 8 via a likewise large-volume pressure medium line 81 and is switched via a pressure medium control line 91, with this line being filled and vented via a solenoid valve 95 which is connected to the system pressure line 76
  • OMPI is.
  • This solenoid valve 95 is switched via an electrical line 97, which is connected to a switch, not shown, in the gear shifting device.
  • a pressure switch 96 is also arranged in this line, which only permits actuation of the solenoid valve 95 if a defined minimum pressure is present in the system pressure line 76.
  • the pulse valve 8 depending on the pressure in the large-volume pressure medium line 81, the system pressure line 76, to which a pressure medium reservoir 75 can also be connected, is connected with this line 81 and the coolant line 73 possibly also with a coolant reservoir 71 the large-volume coolant channel 72, which leads to the disk set 11 of the clutch 1.
  • the pulse valve 8 To control the pulse valve 8, it also has an actuating device 82 for switching on, which is connected directly to the system pressure line 76.
  • the pulse valve 8 is switched off via a compression spring 86 in connection with an actuating device 83, which is located on a bypass 84 which lies between the large-volume pressure medium line 81 and the system pressure line 76, a throttle 85 being arranged between the actuating device 83 and the system pressure line 76 is.
  • the system pressure line 76 is connected directly and the coolant line 73 to a generally known pressure medium pump 7 via a pressure relief valve (not shown).
  • a connecting line with an orifice can also be arranged between the filling and emptying channel for the radially outer pressure chamber 4 and the radially inner pressure chamber 6.
  • a simple pressure relief valve or an end can also be used.
  • FIG. 2 shows a clutch 1 with a clutch carrier 14 driven by the converter turbine.
  • the filling and quick emptying valve 3 is with the clutch carrier 14
  • Clutch 1 e.g. B. connected via fastening screws 390.
  • the piston 31 is arranged in a cylindrical bore 32 in the housing 39 and drawn in the closed position - radially outside -. In In this position, both the radially outer 4 via the filling and emptying duct 41 with the emptying opening 35 and the radially inner pressure chamber 6 via the emptying duct 61 with the emptying opening 36 are very short and large in cross section. Both pressure chambers 4, 6 act on the disk pack 11 via the pressure piston 12.
  • the emptying openings 35 and 36 are arranged in the housing 39 of the filling and sniping discharge valve 3.
  • the spring 33 also pushes the piston 31 radially outward when no centrifugal force is acting.
  • the control line 37 is connected to the chamber 2 and interacts with the outer piston surface 34. 15 is the fixed housing of the clutch 1, the output of which takes place via the inner disk carrier 16.
  • control valve 5 is mounted on the coupling carrier 14 and connects the filling and emptying channel 41 via the supply line 56 when the pressure in the radially outer pressure chamber 4 has reached a predetermined value, with the radially inner pressure chamber 6 Via the filling channel 62 for filling it and for transmitting the maximum possible engine torque via both pressure chambers and the clutch 1.
  • housing 57 of the control valve 5 "there is a cylindrical bore 52 which runs in the radial direction. A piston 51 in this bore 52 is also pushed radially outwards without the action of centrifugal force by a compression spring 53.
  • the pressure from the radially outer pressure chamber 4 also acts on the outer piston surface 54 via the control line 55 and presses the piston 51 radially inward, via this control valve 5 the two pressure chambers 4, 6 are connected via lines 41, 55/56, 62 when the clutch 1, below he the effect of both pressure chambers 4, 6 is closed.
  • FIG. 4 and 5 show the transmission torques M- of the clutch 1 as a function of the pressure chambers 4 and 6 and the number of revolutions / minute of the clutch carrier 14, with FIG. 4 referring to the radially outer 4 and FIG. 5 relates the radially inner pressure chamber 6.
  • the transmission torques are calculated on the basis of fixed and identical friction surfaces, friction pairings and friction values of the same switching and spring pressure, taking into account the piston surfaces which result in connection with the pressure chambers 4, 6.
  • the control device operates as follows: If a gearshift is to be initiated in the countershaft transmission, the circuit in line 97 is interrupted by a switch in the gearshifting device, which is not shown, and the solenoid valve 95 shuts off the system pressure line 76 and vents the pressure medium control line 91, so that the switching valve 9 also vents the chamber 2. Since the pressure in the control line 37 collapses, the filling and line emptying valve 3 is brought into the position shown and both pressure chambers 4 and 6 are emptied to the openings 35, 36 via the lines 41, 61 provided with large cross sections.
  • the actuating device 82 switches the pulse valve 8 to flow, so that the chamber 2 is suddenly filled with pressure medium from the system pressure line 76 and from the pressure medium dispenser 75 and, due to the pressure increase via the control line 37, the filling and rapid emptying valve 3 is also set to flow , so that the radially outer pressure space is filled and the pressure piston 12 engages the plates (plate pack 11).
  • the coolant line 73 with the coolant reservoir 71 has been suddenly connected to the coolant channel 72, so that the slats which are in contact but are still slipping are optimally lubricated and cooled.
  • the radially inner pressure chamber 6 is filled via the control line 55 via the control valve 5 and the feed line 56 and the filling channel 62, so that the maximum possible transmission torque is reached via both pressure chambers 4, 6.
  • this pulse valve is closed via the actuating device 83 and the spring 8 (,), so that both stores 71, 75 can refill.
  • the leakage loss is compensated via the throttle 85 and the system pressure line 76.
  • the system pressure, line 76, is superimposed in the area of the chamber 2 and the pressure chambers 4 to 6 by a centrifugal force-dependent pressure so that, depending on the speed, the clutch carrier 14 also has a higher speed 4 and 5 result in higher transmission torques, in this way in particular the driving state - train / push - is taken into account when switching with the pressure medium itself.
  • the application is not limited to the exemplary embodiment shown. So it is z. B. also possible to switch the switching valve 9 to flow when the solenoid valve 95 has interrupted the system pressure and the pressure medium control line 91 is interrupted.

Landscapes

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

Abstract

Dispositif de commande pour un embrayage (1) avec convertisseur de couple situé dans une construction commune avec une transmission à engrenages synchronisée, l'embrayage étant fermé au moyen d'une commande de l'installation de changement des rapports par deux chambres de pression (4, 6) disposées radialement en parallèle, en fonction de la vitesse de rotation comme de l'état de marche, avec un couplage faible puis, après une vidange rapide, ouvert par effet de ressort. On commence par remplir la chambre de pression radialement extérieure (4) avant de superposer à la pression de commutation - pression du système - une pression dépendant de la force centrifuge et présente dans les deux chambres de pression, de telle façon que, en fonction de cette force centrifuge, se créent des moments de transfert différents qui agissent en particulier aussi en cas de traction (vitesse de rotation élevée) et de poussée (ralenti). Les chambres de pression (4, 6) sont reliées sur de grandes sections transversales (41, 61) à une soupape de remplissage et de vidange (3), grâce à laquelle est remplie et vidéela chambre de pression radialement extérieure (4), alors que la chambre de pression radialement intérieure (6) n'est que vidée. Ainsi, il est possible de simplifier la commande qui est fonction de l'état de marche lors d'une pression du système relativement basse à la suite du transfert de pression dépendant de la force centrifuge, et de l'accélérer par la vidange des deux chambres de pression également jusqu'au transfert du couple moteur maximal possible.
PCT/EP1984/000003 1983-02-22 1984-01-04 Dispositif de commande pour embrayage WO1984003337A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
BR8406983A BR8406983A (pt) 1983-02-22 1984-01-04 Conjunto de comando para um acoplamento de comando

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE3305999A DE3305999C1 (de) 1983-02-22 1983-02-22 Steuereinrichtung fuer eine Schaltkupplung

Publications (1)

Publication Number Publication Date
WO1984003337A1 true WO1984003337A1 (fr) 1984-08-30

Family

ID=6191427

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1984/000003 WO1984003337A1 (fr) 1983-02-22 1984-01-04 Dispositif de commande pour embrayage

Country Status (7)

Country Link
EP (1) EP0166722A1 (fr)
JP (1) JPS60500634A (fr)
BR (1) BR8406983A (fr)
DE (1) DE3305999C1 (fr)
IT (1) IT1173094B (fr)
WO (1) WO1984003337A1 (fr)
ZA (1) ZA84627B (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62292927A (ja) * 1986-06-10 1987-12-19 Honda Motor Co Ltd 油圧クラツチ
US4875561A (en) * 1987-10-09 1989-10-24 Borg-Warner Automotive, Inc. Dual clutch application area and control
SE524472C2 (sv) * 2002-12-06 2004-08-10 Haldex Traction Ab Anordning för att överföra moment mellan två roterbara, koaxiella axelelement
AT8780U1 (de) 2005-05-31 2006-12-15 Magna Drivetrain Ag & Co Kg Reibungskupplung mit hydraulischem aktuator und antriebseinheit mit mindestens einer solchen
US9835207B2 (en) 2013-02-26 2017-12-05 Borgwarner Torqtransfer Systems Ab Method for operating a hydraulic disc coupling in an AWD vehicle and a coupling therefore

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1555340B2 (de) * 1963-10-04 1976-01-15 Ford-Werke AG, 5000Köln Hydraulisch betaetigte reibungskupplung, insbesondere fuer automatische getriebe von kraftfahrzeugen
DE2714500B1 (de) * 1977-04-01 1977-11-10 Bayerische Motoren Werke Ag Hydraulisch betaetigte Reibungskupplung,insbesondere Lamellenkupplung fuer automatische Getriebe von Kraftfahrzeugen
GB1492568A (en) * 1974-12-05 1977-11-23 Honda Motor Co Ltd Safety apparatus in automatic transmission apparatus for vehicle
DE2941935A1 (de) * 1979-10-17 1981-04-30 Zahnradfabrik Friedrichshafen Schaltkupplung mit drehmomentwandler

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1555340B2 (de) * 1963-10-04 1976-01-15 Ford-Werke AG, 5000Köln Hydraulisch betaetigte reibungskupplung, insbesondere fuer automatische getriebe von kraftfahrzeugen
GB1492568A (en) * 1974-12-05 1977-11-23 Honda Motor Co Ltd Safety apparatus in automatic transmission apparatus for vehicle
DE2714500B1 (de) * 1977-04-01 1977-11-10 Bayerische Motoren Werke Ag Hydraulisch betaetigte Reibungskupplung,insbesondere Lamellenkupplung fuer automatische Getriebe von Kraftfahrzeugen
DE2941935A1 (de) * 1979-10-17 1981-04-30 Zahnradfabrik Friedrichshafen Schaltkupplung mit drehmomentwandler

Also Published As

Publication number Publication date
ZA84627B (en) 1984-09-26
BR8406983A (pt) 1985-06-11
IT8419257A0 (it) 1984-01-20
JPS60500634A (ja) 1985-05-02
IT1173094B (it) 1987-06-18
DE3305999C1 (de) 1984-05-10
EP0166722A1 (fr) 1986-01-08

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